CN108139120B

CN108139120B - Air conditioner

Info

Publication number: CN108139120B
Application number: CN201680059961.7A
Authority: CN
Inventors: 池田宗史; 若本慎一; 竹中直史; 鸠村杰
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2015-10-21
Filing date: 2016-09-23
Publication date: 2020-04-17
Anticipated expiration: 2036-09-23
Also published as: CN108139120A; EP3367020A4; WO2017068909A1; JP6479204B2; JPWO2017068909A1; US20190049154A1; US10845095B2; EP3367020B1; EP3367020A1

Abstract

The air conditioner is provided with: a refrigerant circuit in which a compressor, a flow switching device, a heat source-side heat exchanger, a throttle device, a load-side heat exchanger, and the flow switching device are connected in this order by piping, and which is capable of performing an operation in which a cooling operation and a heating operation are switched by the flow switching device; an oil separator for separating the refrigerating machine oil from the refrigerant discharged from the compressor; a 1 st bypass flow path for introducing the fluid flowing out of the oil separator; an auxiliary heat exchanger for cooling fluid; a 1 st flow rate adjusting device for controlling the passage of the fluid; a 2 nd bypass passage for introducing a liquid refrigerant or a two-phase refrigerant of liquid and gas flowing through a pipe connecting the heat source side heat exchanger and the expansion device; and a 2 nd flow rate adjusting device for controlling the passing of the refrigerant.

Description

Air conditioner

Technical Field

The present invention relates to an air conditioner capable of suppressing an increase in the discharge temperature of a compressor.

Background

Conventionally, an air conditioner has been known which cools refrigerating machine oil discharged from a compressor and returns the oil to a suction side of the compressor (see, for example, patent document 1). In the conventional air conditioner described in patent document 1, the influence of heating on the refrigerant circuit is measured by detecting a temperature difference in which the temperature of the suction gas increases due to return oil heating, and the flow rate adjusting device is controlled.

Prior art documents

Patent document

Patent document 1: japanese patent laid-open publication No. 2011-89736

Disclosure of Invention

Problems to be solved by the invention

However, in the conventional air-conditioning apparatus as described in patent document 1, for example, when a refrigerant whose discharge temperature is likely to increase is used, there is a possibility that the increase in the discharge temperature of the compressor cannot be suppressed.

The present invention has been made in view of the above-described problems, and an object of the present invention is to provide an air conditioner capable of suppressing an increase in the discharge temperature of a compressor.

Means for solving the problems

The air conditioner of the invention comprises: a refrigerant circuit in which a compressor, a flow switching device, a heat source side heat exchanger, a throttle device, a load side heat exchanger, and the flow switching device are connected in this order by piping, and an operation is performed such that the flow switching device can switch between a cooling operation in which a discharge side of the compressor is connected to the heat source side heat exchanger and a suction side of the compressor is connected to the load side heat exchanger, and a heating operation in which the discharge side of the compressor is connected to the load side heat exchanger and the suction side of the compressor is connected to the heat source side heat exchanger; an oil separator disposed in the pipe connecting the discharge portion of the compressor and the flow path switching device, for separating the refrigerating machine oil from the refrigerant discharged from the compressor; a 1 st bypass flow path which is connected to an oil outflow side of the oil separator and an intake portion of the compressor and which introduces a fluid flowing out of the oil separator; an auxiliary heat exchanger disposed in the 1 st bypass passage and cooling the fluid; a 1 st flow rate adjusting device disposed in the 1 st bypass flow path and controlling passage of the fluid; a 2 nd bypass passage connected to the pipe connecting the heat source side heat exchanger and the expansion device and the pipe connecting the suction portion of the compressor and the passage switching device, and configured to introduce a liquid refrigerant or a two-phase refrigerant of a liquid and a gas flowing through the pipe connecting the heat source side heat exchanger and the expansion device; and a 2 nd flow rate adjusting device disposed in the 2 nd bypass flow path and controlling the passage of the refrigerant.

Effects of the invention

According to the present invention, it is possible to obtain an air conditioning apparatus in which the opening degree of the 1 st flow rate adjusting device is adjusted using the temperature detected by the discharge temperature sensor, and therefore, the increase in the discharge temperature of the compressor is suppressed.

Drawings

Fig. 1 is a diagram schematically illustrating an example of a circuit configuration of an air conditioning apparatus according to embodiment 1 of the present invention.

Fig. 2 is a diagram illustrating an example of the flow of the refrigerant in the cooling operation mode of the air conditioning apparatus shown in fig. 1.

Fig. 3 is a diagram illustrating an example of the flow of the refrigerant in the heating operation mode of the air conditioning apparatus shown in fig. 1.

Fig. 4 is a diagram illustrating an example of a relationship among the opening degree of the 1 st flow rate adjustment device illustrated in fig. 1, the temperature of the fluid passing through the auxiliary heat exchanger, and the state of the fluid flowing through the 1 st bypass passage.

Fig. 5 is a diagram illustrating an example of a relationship between the opening degree of the 1 st flow rate adjustment device shown in fig. 1 and the capacity of the auxiliary heat exchanger.

Fig. 6 is a diagram illustrating an example of the operation of the air conditioner shown in fig. 1.

Fig. 7 is a diagram schematically illustrating an example of a circuit configuration of an air conditioning apparatus according to embodiment 2 of the present invention.

Fig. 8 is a diagram schematically illustrating an example of a circuit configuration of an air conditioning apparatus according to embodiment 3 of the present invention.

Fig. 9 is a diagram illustrating an example of the operation of the air conditioner shown in fig. 8.

Fig. 10 is a diagram illustrating the process 1 shown in fig. 9.

Fig. 11 is a diagram schematically illustrating an example of a circuit configuration of an air conditioning apparatus according to embodiment 4 of the present invention.

Fig. 12 is a diagram schematically illustrating an example of the circuit configuration of an air conditioning apparatus according to embodiment 5 of the present invention.

Fig. 13 is a diagram illustrating an example of the flow of the refrigerant in the cooling only operation mode of the air conditioning apparatus illustrated in fig. 12.

Fig. 14 is a diagram illustrating an example of the flow of the refrigerant in the cooling main operation mode of the air conditioning apparatus illustrated in fig. 12.

Fig. 15 is a diagram illustrating an example of the flow of the refrigerant in the heating only operation mode of the air conditioning apparatus illustrated in fig. 12.

Fig. 16 is a diagram illustrating an example of the flow of the refrigerant in the heating main operation mode of the air conditioning apparatus illustrated in fig. 12.

Fig. 17 is a diagram schematically illustrating an example of the circuit configuration of an air conditioner according to embodiment 6 of the present invention.

Fig. 18 is a diagram schematically illustrating an example of the circuit configuration of an air conditioning apparatus according to embodiment 7 of the present invention.

Fig. 19 is a diagram schematically illustrating an example of the circuit configuration of an air conditioning apparatus according to embodiment 8 of the present invention.

Fig. 20 is a diagram illustrating an example of the operation of the air conditioning apparatus shown in fig. 19 in the cooling only operation mode.

Fig. 21 is a diagram illustrating an example of an operation in the cooling main operation mode of the air conditioner illustrated in fig. 19.

Fig. 22 is a diagram illustrating an example of an operation in the heating only operation mode of the air conditioner illustrated in fig. 19.

Fig. 23 is a diagram illustrating an example of an operation in the heating main operation mode of the air conditioning apparatus illustrated in fig. 19.

Fig. 24 is a diagram schematically illustrating an example of a circuit configuration of an air conditioning apparatus according to embodiment 9 of the present invention.

Fig. 25 is a diagram schematically illustrating an example of the circuit configuration of an air conditioning apparatus according to embodiment 10 of the present invention.

Fig. 26 is a diagram schematically illustrating the configuration of a control device of an air conditioner according to embodiments 1 to 10 of the present invention.

Detailed Description

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the drawings, the same or corresponding portions are denoted by the same reference numerals, and the description thereof will be omitted or simplified as appropriate. The configuration described in each drawing can be appropriately changed in shape, size, arrangement, and the like within the scope of the present invention.

Embodiment 1.

[ air-conditioning apparatus ]

Fig. 1 is a diagram schematically illustrating an example of a circuit configuration of an air conditioning apparatus according to embodiment 1 of the present invention. The air conditioner 100 of the embodiment includes a refrigerant circuit 15 formed by connecting the outdoor unit 1 and the

indoor units

2a and 2b to each other through the main pipe 3 and the

branch pipes

4a and 4 b. Fig. 1 shows an example in which 2

indoor units

2a and 2b are connected in parallel to the outdoor unit 1 via a

main pipe

3 and 2

branch pipes

4a and 4b, and the number of the indoor units may be 1 or 3 or more.

[ outdoor machine ]

The outdoor unit 1 is installed outside a room, for example, and functions as a heat source unit that discharges or supplies heat of an air conditioner. The outdoor unit 1 is equipped with, for example, a compressor 10, an oil separator 11, a refrigerant flow switching device 12, a heat source side heat exchanger 13, an accumulator 16, a 1 st bypass flow path 70, an auxiliary heat exchanger 71, and a 1 st flow rate adjusting device 72, and these are connected by pipes. Further, a fan 14, which is a blower fan that blows air to the heat source side heat exchanger 13 and the auxiliary heat exchanger 71, is mounted in the outdoor unit 1.

The compressor 10 sucks and compresses a refrigerant to a high-temperature and high-pressure state, and is configured by, for example, an inverter compressor or the like whose capacity can be controlled. The compressor 10 preferably has a low-pressure casing structure in which a compression chamber is provided in a closed container, for example, and a low-pressure refrigerant pressure environment is provided in the closed container to suck and compress a low-pressure refrigerant in the closed container.

The oil separator 11 separates the refrigerant discharged from the compressor 10 from the refrigerating machine oil, and is configured by, for example, a cyclone-type oil separator. The refrigerant flow switching device 12 is configured by, for example, a four-way valve or the like, and switches between a refrigerant flow in the heating operation mode and a refrigerant flow in the cooling operation mode. The cooling operation mode is a case where the heat source side heat exchanger 13 functions as a condenser or a gas cooler, and the heating operation mode is a case where the heat source side heat exchanger 13 functions as an evaporator. The heating operation mode is a heating operation mode in the heating chamber, and the cooling operation mode is a cooling operation mode in the cooling chamber.

The heat source side heat exchanger 13 functions as an evaporator in the heating operation mode and functions as a condenser in the cooling operation mode, and exchanges heat between air supplied from, for example, the fan 14 and the refrigerant. The accumulator 16 is provided at a suction portion, which is a suction side of the compressor 10, and accumulates surplus refrigerant generated by a difference between the heating operation mode and the cooling operation mode or surplus refrigerant generated by a transient operation change.

The auxiliary heat exchanger 71 functions as a cooler or a condenser in both the heating operation mode and the cooling operation mode, and exchanges heat between the air supplied from the fan 14 and the refrigerant, for example. The auxiliary heat exchanger 71 cools the refrigerating machine oil when only the refrigerating machine oil flows therethrough, and cools and condenses the refrigerating machine oil and the refrigerant when both the refrigerating machine oil and the refrigerant flow therethrough. For example, the heat source side heat exchanger 13 and the auxiliary heat exchanger 71 have a structure in which heat transfer tubes having different refrigerant flow paths are attached to a common heat transfer fin. That is, the plurality of heat transfer fins are disposed adjacent to each other so as to face the same direction, and the plurality of heat transfer tubes are often inserted into the heat transfer fins. The heat transfer tube of the heat source side heat exchanger 13 and the heat transfer tube of the auxiliary heat exchanger 71, which are provided on the same heat transfer fin, are in an independent state. For example, the heat source side heat exchanger 13 is disposed on the upper side, the auxiliary heat exchanger 71 is disposed on the lower side, and the plurality of heat transfer fins are shared. Thus, the air around the heat source-side heat exchanger 13 and the auxiliary heat exchanger 71 flows to both the heat source-side heat exchanger 13 and the auxiliary heat exchanger 71. For example, the heat transfer area of the auxiliary heat exchanger 71 is smaller than the heat transfer area of the heat source-side heat exchanger 13, and the auxiliary heat exchanger 71 is formed to have a smaller heat exchange amount than the heat source-side heat exchanger 13.

The 1 st bypass passage 70 is configured by a pipe, and allows high-temperature refrigerator oil and high-temperature, high-pressure refrigerant to flow into the auxiliary heat exchanger 71, and allows the refrigerator oil and refrigerant cooled by the auxiliary heat exchanger 71 to flow into the suction portion of the compressor 10. The refrigerant is cooled and condensed by the auxiliary heat exchanger 71. One end of the 1 st bypass passage 70 is connected to the oil outflow side of the oil separator 11, and the other end is connected to the suction pipe 17 between the compressor 10 and the accumulator 16.

The 1 st bypass flow path 70 is provided with a 1 st flow rate adjusting device 72. The 1 st flow rate adjusting device 72 is composed of a device such as an electronic expansion valve, for example, which can variably control the opening degree, and is provided on the outlet side of the auxiliary heat exchanger 71. The 1 st flow rate adjusting device 72 adjusts the flow rates of the refrigerating machine oil and the liquid refrigerant that are cooled and condensed by the auxiliary heat exchanger 71 and then flow into the suction portion of the compressor 10.

The outdoor unit 1 includes a high pressure detection sensor 79, a discharge temperature sensor 80, a refrigerating machine oil temperature sensor 81, a low pressure detection sensor 82, an auxiliary heat exchanger outlet temperature sensor 83, and an outside air temperature sensor 96. The high pressure detection sensor 79 detects a high pressure on the discharge side of the compressor 10. The discharge temperature sensor 80 detects the temperature of the high-temperature and high-pressure refrigerant discharged from the compressor 10. The refrigerating machine oil temperature sensor 81 detects the temperature of the refrigerating machine oil in the casing of the compressor 10. The refrigerating machine oil temperature sensor 81 may detect the temperature of the outer surface of the casing of the compressor 10, and in this case, the temperature of the refrigerating machine oil in the casing of the compressor 10 is detected in a simulated manner. The low pressure detection sensor 82 detects a low pressure of the refrigerant on the suction side of the compressor 10. The auxiliary heat exchanger outlet temperature sensor 83 detects the temperature of the fluid that has exchanged heat in the auxiliary heat exchanger 71. The outdoor air temperature sensor 96 is provided in the air intake portion of the heat source side heat exchanger 13, and detects the temperature around the outdoor unit 1.

[ indoor machine ]

The

indoor units

2a and 2b are installed in a room, for example, inside a room, and supply conditioned air to the room. The

indoor units

2a and 2b include load-

side expansion devices

20a and 20b and load-

side heat exchangers

21a and 21 b. The load-

side expansion devices

20a and 20b function as a pressure reducing valve or an expansion valve that reduces and expands the pressure of the refrigerant. The load-

side expansion devices

20a and 20b are preferably configured by devices such as electronic expansion valves, which can variably control the opening degree. The load-

side expansion devices

20a and 20b are provided upstream of the load-

side heat exchangers

21a and 21b in the cooling only operation mode. The load

side heat exchangers

21a and 21b are connected to the outdoor unit 1 via the main pipe 3 and the

branch pipes

4a and 4 b. The load

side heat exchangers

21a and 21b generate heating air or cooling air to be supplied to the indoor space by exchanging heat between air and the refrigerant. The fan 22 blows indoor air to the load

side heat exchangers

21a and 21 b.

The

indoor units

2a and 2b have an inlet-side temperature sensor 85 and an outlet-side temperature sensor 84. The inlet-side temperature sensor 85 is composed of, for example, a thermistor, and detects the temperature of the refrigerant flowing into the load-

side heat exchangers

21a and 21 b. The inlet-side temperature sensor 85 is provided in the piping on the inlet side of the refrigerant in the load-

side heat exchangers

21a and 21 b. The outlet-side temperature sensor 84 is configured by, for example, a thermistor, and detects the temperature of the refrigerant flowing out of the load-

side heat exchangers

21a and 21 b. The outlet-side temperature sensor 84 is provided on the outlet side of the refrigerant in the load-

side heat exchangers

21a, 21 b.

The control device 97 performs overall control of the air conditioner 100, and is configured to include, for example, an analog circuit, a digital circuit, a CPU, or a combination of 2 or more of these. The control device 97 controls the driving frequency of the compressor 10, the rotation speed (including on/off switching) of the fan 14, switching of the refrigerant flow path switching device 12, the opening degree of the 1 st flow rate adjusting device 72, the opening degrees of the load-

side expansion devices

20a and 20b, and the like based on, for example, detection information detected by the various sensors described above and an instruction from an input device such as a remote controller, and executes each operation mode described later. Although fig. 1 illustrates the case where the control device 97 is provided in the outdoor unit 1, the control device 97 may be provided in each of the outdoor unit 1 and the

indoor units

2a and 2b, or may be provided in at least one of the

indoor units

2a and 2 b.

[ operating modes of air-conditioning apparatus ]

Next, each operation mode executed by the air-conditioning apparatus 100 will be described. The air conditioning apparatus 100 performs the cooling operation and the heating operation in the

indoor units

2a and 2b based on the instructions from the

indoor units

2a and 2 b. The operation modes executed by the air-conditioning apparatus 100 in fig. 1 include a cooling operation mode in which all the

indoor units

2a and 2b that are being driven perform a cooling operation, and a heating operation mode in which all the

indoor units

2a and 2b that are being driven perform a heating operation. Hereinafter, each operation mode and the flow of the refrigerant will be described.

[ refrigeration operation mode ]

Fig. 2 is a diagram illustrating an example of the flow of the refrigerant in the cooling operation mode of the air conditioning apparatus shown in fig. 1. In the example shown in fig. 2, a cooling only operation mode in which a cooling load is generated in the load

side heat exchangers

21a and 21b will be described. In fig. 2, for easy understanding of the present embodiment, the flow direction of the refrigerant flowing through the refrigerant circuit 15 is indicated by solid arrows, and the flow direction of the refrigerating machine oil and the refrigerant flowing through the 1 st bypass passage 70 is indicated by double-line arrows.

First, the flow of the refrigerant in the refrigerant circuit 15 will be described. The compressor 10 sucks and compresses a low-temperature and low-pressure refrigerant, and discharges a high-temperature and high-pressure refrigerant. The high-temperature and high-pressure refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 13 via the oil separator 11 and the refrigerant flow switching device 12. The refrigerant flowing into the heat source side heat exchanger 13 exchanges heat with outdoor air supplied from the fan 14 and condenses. The refrigerant condensed in the heat source side heat exchanger 13 flows out of the outdoor unit 1, passes through the main pipe 3 and the

branch pipes

4a and 4b, and flows into the

indoor units

2a and 2 b.

The refrigerant flowing into the

indoor units

2a and 2b is expanded by the load-

side expansion devices

20a and 20 b. The refrigerant expanded by the load-

side expansion devices

20a and 20b flows into the load-

side heat exchangers

21a and 21b functioning as evaporators, and absorbs heat from the indoor air to be evaporated. In the load

side heat exchangers

21a and 21b, the refrigerant absorbs heat from the indoor air, and the indoor air is cooled. At this time, the opening degrees of the load-

side throttles

20a and 20b are controlled by the controller 97 so that the degree of superheat (superheat) is constant. The degree of superheat is obtained by using the difference between the temperature detected by the inlet-side temperature sensor 85 and the temperature detected by the outlet-side temperature sensor 84. The refrigerant flowing out of the load

side heat exchangers

21a and 21b passes through the

branch pipes

4a and 4b and the main pipe 3, and flows into the outdoor unit 1 again. The refrigerant flowing into the outdoor unit 1 passes through the refrigerant flow switching device 12 and the accumulator 16, is again sucked into the compressor 10, and is compressed.

Next, the flow of the refrigerating machine oil is shown as follows. The refrigerating machine oil accumulated in the casing of the compressor 10 is heated by the refrigerant to a temperature equal to that of the refrigerant, and is discharged from the compressor 10. The high-temperature refrigerator oil discharged from the compressor 10 and a part of the gas refrigerant are separated by the oil separator 11, and flow into the auxiliary heat exchanger 71 through the 1 st bypass passage 70. The refrigerating machine oil and the gas refrigerant flowing through the auxiliary heat exchanger 71 are cooled and condensed to the same temperature as the outdoor air while releasing heat to the outdoor air supplied from the fan 14. The refrigerating machine oil and the liquid refrigerant flowing out of the auxiliary heat exchanger 71 are again sucked into the compressor 10 by the 1 st flow rate adjusting device 72.

[ Effect in the Cooling operation mode ]

As described above, in the outdoor unit 1 of the example of the present embodiment, in the cooling operation mode, part of the refrigerator oil and the gas refrigerant separated by the oil separator 11 flows into the auxiliary heat exchanger 71 through the 1 st bypass passage 70. The refrigerating machine oil and the refrigerant flowing through the auxiliary heat exchanger 71 are cooled by heat exchange with the outdoor air supplied from the fan 14. The refrigerating machine oil and the refrigerant cooled by the auxiliary heat exchanger 71 flow into the suction portion of the compressor 10 through the 1 st flow rate adjusting device 72. As described above, according to the outdoor unit 1 of the present embodiment, when the discharge temperature of the discharge side of the compressor 10 increases, the refrigerating machine oil and the refrigerant cooled by the auxiliary heat exchanger 71 can be made to flow into the suction side of the compressor 10. As a result, according to the outdoor unit 1 of the present embodiment, since the refrigerant having a reduced enthalpy of suction to the compressor 10 flows into the suction portion of the compressor 10, an increase in the discharge temperature of the compressor 10 can be suppressed. According to the outdoor unit 1 of the present embodiment, since an increase in the discharge temperature of the compressor 10 is suppressed, it is possible to suppress deterioration of the refrigerating machine oil, deterioration of the compressor 10, damage to the compressor, and the like. Further, according to the outdoor unit 1 of the example of the present embodiment, since an increase in the discharge temperature of the compressor 10 is suppressed, the rotational speed of the compressor 10 can be increased to improve the cooling capacity. As a result, the comfort of the user using the air conditioner 100 can be improved. In particular, when the refrigerant applied to the air conditioner 100 is a refrigerant having a higher discharge temperature of the compressor 10 than that of the compressor 10 such as R410A refrigerant (hereinafter, referred to as R410A) like R32 refrigerant (hereinafter, referred to as R32), for example, the effect of suppressing the risk of degradation of the refrigerating machine oil and the risk of degradation and damage of the compressor 10 becomes remarkable. Further, according to the outdoor unit 1 of the example of the present embodiment, even when the discharge temperature of the compressor 10 is low, the loss due to suction heating can be suppressed by flowing the cooled refrigerating machine oil into the suction portion of the compressor 10.

[ heating operation mode ]

Fig. 3 is a diagram illustrating an example of the flow of the refrigerant in the heating operation mode of the air conditioning apparatus shown in fig. 1. In fig. 3, the heating only operation mode will be described by taking as an example a case where a heating load is generated in the load

side heat exchangers

21a and 21 b. In fig. 3, for easy understanding of the present embodiment, the flow direction of the refrigerant flowing through the refrigerant circuit 15 is indicated by solid arrows, and the flow direction of the refrigerating machine oil and the refrigerant flowing through the 1 st bypass passage 70 is indicated by double-line arrows.

First, the flow of the refrigerant in the refrigerant circuit 15 will be described. The compressor 10 sucks and compresses a low-temperature and low-pressure refrigerant, and discharges a high-temperature and high-pressure refrigerant. The high-temperature and high-pressure refrigerant discharged from the compressor 10 passes through the oil separator 11 and the refrigerant flow switching device 12 and flows out of the outdoor unit 1. The high-temperature and high-pressure refrigerant flowing out of the outdoor unit 1 passes through the main pipe 3 and the

branch pipes

4a and 4b, releases heat to the indoor air in the load

side heat exchangers

21a and 21b, and condenses while heating the indoor space. The refrigerant condensed in the load

side heat exchangers

21a and 21b is expanded by the load

side expansion devices

20a and 20b, passes through the

branch pipes

4a and 4b and the main pipe 3, and again flows into the outdoor unit 1. The refrigerant flowing into the outdoor unit 1 flows into the heat source side heat exchanger 13, evaporates while absorbing heat from outdoor air in the heat source side heat exchanger 13, and is again sucked into the compressor 10 via the refrigerant flow switching device 12 and the accumulator 16.

[ Effect during heating operation ]

In the heating operation mode, part of the refrigerating machine oil and the gas refrigerant separated by the oil separator 11 flows into the auxiliary heat exchanger 71 through the 1 st bypass passage 70, as in the cooling operation mode described above. The refrigerating machine oil and the refrigerant flowing through the auxiliary heat exchanger 71 are cooled by heat exchange with the outdoor air supplied from the fan 14. The refrigerating machine oil and the refrigerant cooled by the auxiliary heat exchanger 71 flow into the suction portion of the compressor 10 through the 1 st flow rate adjusting device 72. As described above, according to the outdoor unit 1 of the present embodiment, when the discharge temperature of the discharge side of the compressor 10 increases, the refrigerating machine oil and the refrigerant cooled by the auxiliary heat exchanger 71 can be made to flow into the suction side of the compressor 10. As a result, according to the outdoor unit 1 of the present embodiment, since the refrigerant having a reduced enthalpy of suction to the compressor 10 flows into the suction portion of the compressor 10, an increase in the discharge temperature of the compressor 10 can be suppressed. According to the outdoor unit 1 of the present embodiment, since an increase in the discharge temperature of the compressor 10 is suppressed, it is possible to suppress deterioration of the refrigerating machine oil, deterioration of the compressor 10, damage to the compressor, and the like. Further, according to the outdoor unit 1 of the example of the present embodiment, since an increase in the discharge temperature of the compressor 10 is suppressed, the rotational speed of the compressor 10 can be increased to improve the cooling capacity. As a result, the comfort of the user using the air conditioner 100 can be improved. In particular, when the refrigerant applied to the air conditioner 100 is a refrigerant having a higher discharge temperature of the compressor 10 than that of the compressor 10 such as R410A refrigerant (hereinafter, referred to as R410A) like R32 refrigerant (hereinafter, referred to as R32), for example, the effect of suppressing the risk of degradation of the refrigerating machine oil and the risk of degradation and damage of the compressor 10 becomes remarkable. Further, according to the outdoor unit 1 of the example of the present embodiment, even when the discharge temperature of the compressor 10 is low, the loss due to suction heating can be suppressed by flowing the cooled refrigerating machine oil into the suction portion of the compressor 10.

[ operation of the 1 st flow rate adjusting device 72 ]

Next, the operation of the 1 st flow rate adjusting device 72 will be described. The 1 st flow rate adjusting device 72 is controlled by, for example, a control device 97. The 1 st flow rate adjusting device 72 is controlled based on, for example, the discharge temperature of the compressor 10 detected by the discharge temperature sensor 80.

First, an example of the correlation between the opening degree of the 1 st flow rate adjustment device 72 and the discharge temperature of the refrigerant discharged from the compressor 10 will be described. When the opening degree (opening area) of the 1 st flow rate adjustment device 72 is increased, the flow rates of the refrigerating machine oil and the liquid refrigerant flowing into the suction portion of the compressor 10 through the auxiliary heat exchanger 71 of the 1 st bypass passage 70 are increased. As a result, the temperature or dryness of the refrigerant at the suction portion of the compressor 10 decreases, and therefore, the discharge temperature of the compressor 10 tends to decrease. On the other hand, when the opening degree (opening area) of the 1 st flow rate adjustment device 72 is decreased, the flow rates of the refrigerating machine oil and the liquid refrigerant flowing into the suction portion of the compressor 10 through the auxiliary heat exchanger 71 of the 1 st bypass passage 70 are decreased. As a result, the temperature or dryness of the refrigerant in the suction portion of the compressor 10 increases, and therefore, the discharge temperature of the compressor 10 increases.

Next, an example of the correlation between the opening degree of the 1 st flow rate adjusting device 72 and the state of the fluid flowing into the 1 st bypass flow path 70 will be described. The state of the fluid flowing into the 1 st bypass flow path 70 changes together with the increase in the flow rate of the fluid flowing into the 1 st bypass flow path 70. For example, when the opening degree of the 1 st flow rate adjustment device 72 is small, only the refrigerating machine oil accumulated in the lower portion of the oil separator 11 flows into the 1 st bypass passage 70. When only the refrigerating machine oil flows into the 1 st bypass passage 70, the amount of the fluid flowing into the 1 st bypass passage 70 is smaller than the amount of the refrigerating machine oil flowing into the oil separator 11. When the opening degree of the 1 st flow rate adjustment device 72 is gradually opened, the refrigerator oil and the gas refrigerant start to flow into the 1 st bypass passage 70. When the refrigerating machine oil and the gas refrigerant flow into the 1 st bypass passage 70, the amount of the fluid flowing into the 1 st bypass passage 70 is larger than the amount of the refrigerating machine oil flowing into the oil separator 11.

Fig. 4 is a diagram illustrating an example of a relationship among the opening degree of the 1 st flow rate adjustment device illustrated in fig. 1, the temperature of the fluid passing through the auxiliary heat exchanger, and the state of the fluid flowing through the 1 st bypass flow path, and fig. 5 is a diagram illustrating an example of a relationship among the opening degree of the 1 st flow rate adjustment device illustrated in fig. 1 and the capacity of the auxiliary heat exchanger. Hereinafter, the correlation between the opening degree of the 1 st flow rate adjusting device 72 and the heat exchange amount of the auxiliary heat exchanger 71 will be described with reference to fig. 4 and 5.

As shown in fig. 4, when the opening degree of the 1 st flow rate adjusting device 72 is K1 or less, the refrigerating machine oil flows into the 1 st bypass flow path 70. The refrigerating machine oil flowing into the 1 st bypass passage 70 is cooled to a temperature close to the air temperature by heat exchange in the auxiliary heat exchanger 71, and flows out of the auxiliary heat exchanger 71.

When the opening degree of the 1 st flow rate adjustment device 72 becomes larger than K1, the refrigerator oil and the gas refrigerant flow into the 1 st bypass passage 70.

When the opening degree of the 1 st flow rate adjustment device 72 is greater than K1 and equal to or less than K3, the refrigerating machine oil and the gas refrigerant that have flowed into the 1 st bypass passage 70 exchange heat in the auxiliary heat exchanger 71, and become lower in temperature than the condensation temperature of the refrigerant. When the opening degree of the 1 st flow rate adjustment device 72 is larger than K1 and equal to or smaller than K3, the refrigerant that has exchanged heat in the auxiliary heat exchanger 71 becomes a liquid refrigerant.

When the opening degree of the 1 st flow rate adjustment device 72 is larger than K1 and equal to or smaller than K2, the refrigerating machine oil and the refrigerant that have exchanged heat in the auxiliary heat exchanger 71 are cooled to near the air temperature.

When the opening degree of the 1 st flow rate adjustment device 72 is larger than K2 and equal to or smaller than K3, the temperatures of the refrigerating machine oil and the refrigerant that have exchanged heat in the auxiliary heat exchanger 71 increase as the opening degree of the 1 st flow rate adjustment device 72 increases.

When the opening degree of the 1 st flow rate adjusting device 72 becomes larger than K3, the temperature of the refrigerating machine oil and the refrigerant that have exchanged heat in the auxiliary heat exchanger 71 becomes the condensation temperature of the refrigerant. When the opening degree of the 1 st flow rate adjustment device 72 becomes larger than K3, the refrigerant that has exchanged heat in the auxiliary heat exchanger 71 becomes a two-phase refrigerant.

As described above, when the opening degree of the 1 st flow rate adjustment device 72 is increased to increase the flow rate of the fluid flowing through the 1 st bypass passage 70, the heat exchange amount in the auxiliary heat exchanger 71 is increased. However, if the flow rate of the fluid flowing through the 1 st bypass passage 70 is too high, the amount of heat exchange that the auxiliary heat exchanger 71 can exchange heat has an upper limit, and therefore the refrigerating machine oil and the refrigerant cannot be completely cooled, and the outlet temperature of the auxiliary heat exchanger 71 increases. When the temperatures of the refrigerating machine oil and the liquid refrigerant flowing out of the auxiliary heat exchanger 71 increase, the cooling capacity on the suction side of the cooling compressor 10 does not change even if the flow rate of the fluid flowing through the 1 st bypass passage 70 is further increased, and therefore, there is no effect of lowering the discharge temperature of the compressor 10. In addition, since the gas refrigerant to be flowed into the

indoor units

2a and 2b is additionally bypassed, performance and capacity of the air conditioner 100 are deteriorated.

In the example of the present embodiment, the 1 st flow rate adjustment device 72 is controlled while the upper limit capacity that the auxiliary heat exchanger 71 can handle is grasped. That is, the operation of the 1 st flow rate adjustment device 72 is controlled based on the outlet temperature of the auxiliary heat exchanger 71 detected by the auxiliary heat exchanger outlet temperature sensor 83 provided at the outlet of the auxiliary heat exchanger 71.

Fig. 6 is a diagram illustrating an example of the operation of the air conditioner shown in fig. 1. The controller 97 performs the following control at set intervals (for example, 30 seconds) for example. First, in step S02, the controller 97 acquires the 1 st flow rate adjustment device current opening O1d, which is the current opening of the 1 st flow rate adjustment device 72, the discharge temperature Td, which is the temperature on the discharge side of the compressor 10, the auxiliary heat exchanger outlet side temperature T1, which is the temperature on the outlet side of the auxiliary heat exchanger 71, the outside air temperature Ta, which is the temperature of the outside air, the refrigerator oil temperature Toil, which is the temperature of the refrigerator oil in the casing of the compressor 10, and the discharge side pressure Ps, which is the pressure on the discharge side of the compressor 10. For example, the acquiring unit (not shown) of the control device 97 acquires the 1 st flow rate adjustment device current opening O1d from the 1 st flow rate adjustment device 72, acquires the discharge temperature Td from the discharge temperature sensor 80, acquires the auxiliary heat exchanger outlet-side temperature T1 from the auxiliary heat exchanger outlet temperature sensor 83, acquires the outside air temperature Ta from the outside air temperature sensor 96, acquires the refrigerator oil temperature Toil from the refrigerator oil temperature sensor 81, and acquires the discharge-side pressure Ps from the high-pressure detection sensor 79.

In step S04, control device 97 obtains a condensation temperature CT that is the condensation temperature of the refrigerant. That is, the control device 97 converts the refrigerant condensation temperature CT from the discharge-side pressure Pd.

In step S06, the control device 97 calculates a temperature difference Δ T that is a value obtained by subtracting the outside air temperature Ta from the auxiliary heat exchanger outlet side temperature T1. In step S08, control device 97 compares temperature difference Δ T with temperature difference threshold value Tth. The temperature difference threshold value Tth is a preset value and is stored in a storage unit (not shown). The temperature difference threshold value Tth is, for example, 5 degrees.

In step S08, when the temperature difference Δ T is smaller than the temperature difference threshold value Tth, the process proceeds to step S10, and the controller 97 calculates a discharge temperature adjustment amount Δ Td, which is a value obtained by subtracting the target discharge temperature Tdn from the discharge temperature Td. The target discharge temperature Tdn is a preset value and is a value related to the specification of the compressor 10. The target discharge temperature Tdn is stored in a storage unit (not shown). In step S12, the control device 97 calculates an operation amount Ocon, which is a value obtained by multiplying the discharge temperature adjustment amount Δ Td by the control constant G1. The control constant G1 is a value related to the control amount of the 1 st flow rate adjustment device 72, and is a positive value. The control constant G1 is set in advance and stored in a storage unit (not shown). Therefore, when the discharge temperature adjustment amount Δ Td is positive, that is, the discharge temperature is higher than the discharge temperature target value, the operation amount Ocon of the 1 st flow rate adjustment device 72 is calculated in the opening direction. When the discharge temperature adjustment amount Δ Td is negative, that is, the discharge temperature is lower than the discharge temperature target value, the operation amount Ocon of the 1 st flow rate adjustment device 72 is calculated in the off direction. In step S14, the controller 97 calculates the output opening On, which is a value obtained by adding the operation amount Ocon to the current opening Od, and proceeds to step S16.

In step S08, when the temperature difference Δ T is equal to or greater than the temperature difference threshold value Tth, the current opening degree O1d is maintained, so in step S15, the calculation output opening degree Onex is Od and the process proceeds to step S16.

In step S16, control device 97 calculates a refrigerating machine oil superheat Osh, which is a value obtained by subtracting condensation temperature ET from refrigerating machine oil temperature Toil. In step 18, the control device 97 compares the refrigerator oil superheat Osh with the refrigerator oil superheat threshold OILsh. The refrigerator oil superheat threshold value OILsh is a preset value and is stored in a storage unit (not shown). The refrigerator oil superheat threshold value OILsh is, for example, 30K.

When the refrigerator oil superheat Osh is equal to or less than the refrigerator oil superheat threshold value OILsh in step S18, the process proceeds to step S20, and the controller 97 calculates a refrigerator oil superheat difference Δ Osh, which is a value obtained by subtracting the target refrigerator oil superheat value SHoil from the refrigerator oil superheat Osh. The target value SHoil of the degree of superheat of the refrigerating machine oil is a preset value and is stored in a storage unit (not shown). The target value SHoil of the degree of superheat of the refrigerating machine oil is, for example, 10K.

In step S22, the control device 97 calculates the refrigerating machine oil correction amount Δ oil, which is a value obtained by multiplying the refrigerating machine oil superheat difference Δ Osh by the control constant G2. The control constant G2 is set to: the correction amount of the 1 st flow rate adjusting device 72 is always calculated in the closing direction when the refrigerator oil superheat difference Δ Osh of the refrigerator oil superheat Osh is positive, and the correction amount of the 1 st flow rate adjusting device 72 becomes larger as the refrigerator oil superheat difference Δ Osh becomes smaller, that is, as the refrigerator oil superheat Osh approaches the target value of the refrigerator oil superheat Osh. In addition, the control constant G2 is set to: when the difference Δ Osh in the degree of superheat of the refrigerating machine oil Osh is negative, that is, the degree of superheat of the refrigerating machine oil Osh is lower than the target value of the degree of superheat of the refrigerating machine oil Osh, the correction amount of the 1 st flow rate adjusting device 72 is a fixed value.

In step S24, the controller 97 calculates a corrected opening Oop that is a value obtained by adding the refrigerator oil correction amount Δ oil to the output opening Onex, and proceeds to step S28.

In step S18, when the refrigerator oil superheat Osh is greater than the refrigerator oil superheat threshold value OILsh, the process proceeds to step S24, and the controller 97 calculates the corrected opening degree Oop as the output opening degree Onex and proceeds to step S28.

In step S28, the control device 97 sets the opening degree of the 1 st flow rate adjustment device 72 to the correction opening degree Oop.

In the above description, the case where the temperature difference threshold value Tth is 5 degrees is exemplified, but the temperature difference threshold value Tth is not limited to 5 degrees. That is, when the capacity of the auxiliary heat exchanger 71 reaches the upper limit capacity that can be handled and the refrigerant flowing out of the outlet of the auxiliary heat exchanger 71 is in the two-phase state, the temperature of the outlet of the auxiliary heat exchanger 71 is a saturation temperature corresponding to the high-pressure of the refrigerant flowing into the auxiliary heat exchanger 71. That is, the temperature difference threshold Tth, which is the difference between the auxiliary heat exchanger outlet side temperature T1 and the outside air temperature Ta when the upper limit capacity that the auxiliary heat exchanger 71 can handle, is at most the difference obtained by subtracting the outside air temperature from the condensation temperature, and therefore, the threshold may be set to be equal to or lower than this.

As described above, since the upper limit can be set for the amount of the refrigerating machine oil and the gas refrigerant that bypass the oil separator 11 by adjusting the opening degree of the 1 st flow rate adjusting device 72 in accordance with the outlet temperature of the auxiliary heat exchanger 71, it is possible to prevent excessive bypass and suppress a reduction in the capacity and performance of the air conditioner 100.

Embodiment 2.

Fig. 7 is a diagram schematically illustrating an example of a circuit configuration of an air conditioning apparatus according to embodiment 2 of the present invention. In the air conditioner 101 of fig. 7, the same reference numerals are given to parts having the same configurations as those of the air conditioner 100 of fig. 1, and the description thereof is omitted. In the air conditioner 101 of fig. 7, the outdoor unit 1 is different in configuration from the air conditioner 100 of fig. 1. That is, the outdoor unit 1 of the example of the present embodiment further includes a flow rate adjuster 73 arranged in parallel with the 1 st flow rate adjuster 72. The flow rate adjuster 73 is constituted by a device such as a capillary tube to which a flow path resistance value is fixed. The flow rate adjuster 73 has a flow path resistance smaller than that when the opening degree of the 1 st flow rate adjusting device 72 is in the fully open state, for example. The pipe in which the flow rate regulator 73 is disposed corresponds to the "bypass passage 78" of the present invention. That is, the outdoor unit 1 of the example of the present embodiment may have the bypass passage 78 disposed in parallel with the 1 st flow rate adjustment device 72 and omitting the flow rate adjuster 73.

In the air conditioner 101, for example, when the discharge temperature of the compressor 10 detected by the discharge temperature sensor 80 is equal to or lower than the discharge temperature threshold, the controller 97 controls the 1 st flow rate adjusting device 72 so that the 1 st flow rate adjusting device 72 is in the fully-closed state. The discharge temperature threshold value is, for example, a temperature lower than a temperature at which the compressor 10 is at risk of damage or a temperature at which the refrigerator oil is at risk of degradation, and is set to, for example, 115 degrees or less. The discharge temperature threshold value is set in advance in accordance with a limit value of the discharge temperature of the compressor 10 or the like, and is stored in, for example, a storage unit (not shown).

As described above, since the outdoor unit 1 of the present embodiment includes the flow rate adjuster 73 arranged in parallel with the 1 st flow rate adjuster 72, even if the 1 st flow rate adjuster 72 is in an abnormal state and is in a closed state, the refrigerating machine oil or the refrigerating machine oil and the refrigerant circulate in the order of the compressor 10, the oil separator 11, the auxiliary heat exchanger 71, the flow rate adjuster 73, and the compressor 10. Therefore, even if the 1 st flow rate adjustment device 72 is in the closed state due to an abnormality, the refrigerating machine oil of an amount not to be depleted from the refrigerating machine oil inside the compressor 10 flows into the suction portion of the compressor 10 through the auxiliary heat exchanger 71 and the flow rate adjuster 73. Therefore, according to the outdoor unit 1 of the example of the present embodiment, even when the 1 st flow rate adjustment device 72 is in the closed state due to an abnormality, it is possible to secure the amount of the refrigerating machine oil necessary for lubrication and sealing of the compressor 10 while suppressing an increase in the discharge temperature of the compressor 10. Therefore, according to the outdoor unit 1 of the example of the present embodiment, the risk of damage to the compressor 10 can be reliably suppressed.

Embodiment 3.

Fig. 8 is a diagram schematically illustrating an example of a circuit configuration of an air conditioning apparatus according to embodiment 3 of the present invention. In the air conditioner 102 in fig. 8, the same reference numerals are given to parts having the same configuration as the air conditioner 101 in fig. 7, and the description thereof is omitted. In the air conditioner 102 of fig. 8, the outdoor unit 1 is different in configuration from the air conditioner 101 of fig. 7. That is, the outdoor unit 1 of the present embodiment further includes the 2 nd bypass flow path 74 in which the 2 nd flow rate adjusting device 75 is disposed. One end of the 2 nd bypass passage 74 is connected to a pipe between the heat source side heat exchanger 13, through which the liquid refrigerant or the two-phase refrigerant including the liquid refrigerant flows, and the main pipe 3 in both the cooling operation and the heating operation, and the other end is connected to the outflow side of the 1 st flow control device 72. That is, the 2 nd bypass passage 74 bypasses the piping connecting the heat source side heat exchanger 13 and the load

side expansion devices

20a and 20b and the intake side of the compressor 10. The 2 nd bypass passage 74 is a pipe through which a low-temperature high-pressure liquid refrigerant flows into the suction portion of the compressor 10 during the cooling operation and a medium-temperature medium-pressure liquid refrigerant or two-phase refrigerant flows into the suction portion of the compressor 10 during the heating operation. The 2 nd flow rate adjusting device 75 is composed of a device such as an electronic expansion valve, for example, which can variably control the opening degree, and adjusts the flow rate of the liquid refrigerant or the two-phase refrigerant flowing into the suction portion of the compressor 10.

Further, a pressure adjusting device 76 is disposed between the heat source side heat exchanger 13 and a connection portion upstream of the 2 nd bypass passage 74. That is, the pressure adjustment device 76 is disposed in the pipe connecting the heat source-side heat exchanger 13 and the load-

side expansion devices

20a and 20b at a position closer to the heat source-side heat exchanger 13 than the connection portion connecting the 2 nd bypass passage 74. The pressure adjusting device 76 is configured by a device such as an electronic expansion valve that can variably control the opening degree, and adjusts the pressure in the upstream portion of the 2 nd bypass passage 74 to a medium pressure during heating operation, for example. That is, the pressure adjusting device 76 adjusts the pressure of the liquid refrigerant or the two-phase refrigerant flowing into the 2 nd bypass passage 74. Further, the outdoor unit 1 is provided with a medium pressure detection sensor 77 for detecting a pressure between the outlet of the load-side expansion device 20 and the pressure adjustment device 76.

Next, the flow of the refrigerant in the 2 nd bypass passage 74 in each operation mode executed by the air-conditioning apparatus 102 will be described.

[ refrigeration operation mode ]

In the cooling operation mode, for example, the pressure adjusting device 76 is in a fully open state. Most of the refrigerant flowing out of the heat source side heat exchanger 13 flows out of the outdoor unit 1 through the pressure adjusting device 76, passes through the main pipe 3 and the

branch pipes

4a and 4b, and flows into the indoor unit 2. The refrigerant flowing into the indoor unit 2 is expanded by the load-

side expansion devices

20a and 20b, and exchanges heat in the load-

side heat exchangers

21a and 21 b. The refrigerant having exchanged heat in the load

side heat exchangers

21a and 21b passes through the

branch pipes

A part of the refrigerant flowing out of the heat source side heat exchanger 13 flows into the 2 nd bypass passage 74, and is expanded by the 2 nd flow rate adjustment device 75. The refrigerant expanded by the 2 nd flow rate adjustment device 75 merges with the fluid flowing out of the 1 st flow rate adjustment device 72, then merges with the refrigerant flowing out of the accumulator 16, and is again sucked into the compressor 19.

[ Effect in the Cooling operation mode ]

As described above, in the air-conditioning apparatus 102 of the example of the present embodiment, in the cooling operation mode, the suction enthalpy of the compressor 10 can be reduced by the fluid cooled by the auxiliary heat exchanger 71, and the suction enthalpy of the compressor 10 can be reduced by a part of the refrigerant cooled by the heat source side heat exchanger 13. Therefore, according to the air conditioner 102 of the example of the present embodiment, when the discharge temperature of the compressor 10 increases, the increase in the discharge temperature of the compressor 10 can be suppressed. That is, for example, even when the heat exchange capacity, which is the processing capacity of the auxiliary heat exchanger 71, reaches the upper limit, the 2 nd flow rate adjustment device 75 can be turned on to suppress the increase in the discharge temperature of the compressor 10. According to the air conditioner 102 of the example of the present embodiment, since an increase in the discharge temperature of the compressor 10 can be suppressed, degradation of the refrigerating machine oil and damage to the compressor 10 can be suppressed. Further, since the refrigerating machine oil in the suction portion of the compressor 10 can be reliably cooled, the loss due to the suction heating of the compressor 10 can be suppressed. Furthermore, since the increase in the discharge temperature of the compressor 10 is suppressed, the rotational speed of the compressor 10 can be increased, and the intensity of cooling can be increased.

[ heating operation mode ]

During the heating operation, the pressure adjusting device 76 has, for example, the following opening degrees: the pressure from the outlet of the load-

side expansion device

20a, 20b of the indoor unit 2 to the inlet of the pressure adjusting device 76 is increased to an intermediate pressure. That is, the pressure adjusting device 76 is controlled so that the value detected by the medium pressure detecting sensor 77 becomes a preset pressure value. The opening degree of the pressure adjusting device 76 is controlled based on the intermediate pressure Pm detected by the intermediate pressure detection sensor 77 during the heating operation. Specifically, the control device 97 measures the intermediate pressure Pm by the intermediate pressure detection sensor 77, and controls so that the intermediate pressure Pm satisfies the following expression (1).

Ps＜Pm＜Pd····(1)

Here, Ps is the suction pressure detected by the low pressure detection sensor 82, and Pd is the discharge pressure detected by the high pressure detection sensor 79.

The refrigerant, which has released heat to the indoor air in the load side heat exchanger 21 and has been expanded by the load

side expansion devices

20a and 20b into a gas-liquid two-phase state at an intermediate temperature and pressure, flows into the outdoor unit 1 again through the

branch pipes

4a and 4b and the main pipe 3. The medium-temperature and medium-pressure gas-liquid two-phase refrigerant flowing into the outdoor unit 1 flows into the 2 nd bypass flow path 74, is expanded by the 2 nd flow rate adjustment device 75 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant, merges with the refrigerator oil and the liquid refrigerant flowing out of the 1 st flow rate adjustment device 72, merges with the refrigerant flowing out of the accumulator 16, and is sucked into the compressor 19 again.

[ Effect in heating operation mode ]

In the air-conditioning apparatus 102 of the example of the present embodiment, in the heating operation mode, the suction enthalpy of the compressor 10 can be reduced by the fluid cooled by the auxiliary heat exchanger 71, and the suction enthalpy of the compressor 10 can be reduced by a part of the refrigerant cooled by the heat source side heat exchanger 13. Therefore, according to the air conditioner 102 of the example of the present embodiment, when the discharge temperature of the compressor 10 increases, the increase in the discharge temperature of the compressor 10 can be suppressed. That is, for example, even when the heat exchange capacity, which is the processing capacity of the auxiliary heat exchanger 71, reaches the upper limit, the 2 nd flow rate adjustment device 75 can be turned on to suppress the increase in the discharge temperature of the compressor 10. According to the air conditioner 102 of the example of the present embodiment, since an increase in the discharge temperature of the compressor 10 can be suppressed, degradation of the refrigerating machine oil and damage to the compressor 10 can be suppressed. Further, since the refrigerating machine oil in the suction portion of the compressor 10 can be reliably cooled, the loss due to the suction heating of the compressor 10 can be suppressed. Furthermore, since the increase in the discharge temperature of the compressor 10 is suppressed, the rotational speed of the compressor 10 can be increased, and the intensity of cooling can be increased.

[ operation of the 1 st flow rate adjustment device 72 and the 2 nd flow rate adjustment device 75 ]

Fig. 9 is a diagram illustrating an example of the operation of the air conditioner illustrated in fig. 8, and fig. 10 is a diagram illustrating the process 1 illustrated in fig. 9. The operation of the 1 st flow rate adjustment device 72 and the 2 nd flow rate adjustment device 75 will be described with reference to fig. 9 and 10. The 1 st flow rate adjustment device 72 and the 2 nd flow rate adjustment device 75 control the opening degrees based on, for example, the discharge temperature of the compressor 10 detected by the discharge temperature sensor 80, and switch the control targets of the opening degrees of the 1 st flow rate adjustment device 72 and the 2 nd flow rate adjustment device 75 based on the outlet temperature of the auxiliary heat exchanger 71 detected by the auxiliary heat exchanger outlet temperature sensor 83.

The controller 97 performs the following control at set intervals (for example, 30 seconds) for example. First, in step S02 of fig. 9, the controller 97 acquires the 1 st flow rate adjustment device current opening O1d, which is the current opening of the 1 st flow rate adjustment device 72, the 2 nd flow rate adjustment device current opening O2d, which is the current opening of the 2 nd flow rate adjustment device 75, the discharge temperature Td, which is the temperature on the discharge side of the compressor 10, the auxiliary heat exchanger outlet side temperature T1, which is the temperature on the outlet side of the auxiliary heat exchanger 71, the outside air temperature Ta, which is the temperature of the outside air, the refrigerating machine oil temperature Toil, which is the temperature of the refrigerating machine oil in the casing of the compressor 10, and the discharge side pressure Ps, which is the pressure on the discharge side of the compressor 10. For example, the acquiring unit (not shown) of the control device 97 acquires the 1 st flow rate adjustment device current opening O1d from the 1 st flow rate adjustment device 72, acquires the 2 nd flow rate adjustment device current opening O2d from the 2 nd flow rate adjustment device 75, acquires the discharge temperature Td from the discharge temperature sensor 80, acquires the auxiliary heat exchanger outlet side temperature T1 from the auxiliary heat exchanger outlet temperature sensor 83, acquires the outdoor air temperature Ta from the outdoor air temperature sensor 96, acquires the refrigerator oil temperature Toil from the refrigerator oil temperature sensor 81, and acquires the discharge side pressure Ps from the high pressure detection sensor 79.

In step S06, the control device 97 calculates a temperature difference Δ T that is a value obtained by subtracting the outside air temperature Ta from the auxiliary heat exchanger outlet side temperature T1.

In step S108, the control device 97 compares the temperature difference Δ T with the temperature difference threshold value Tth and determines the on-off state of the 2 nd flow rate adjustment device 75 based on the 2 nd flow rate adjustment device current opening degree O2 d. The temperature difference threshold value Tth is a preset value and is stored in a storage unit (not shown). The temperature difference threshold value Tth is, for example, 5 degrees. If the temperature difference Δ T is smaller than the temperature difference threshold value Tth and the 2 nd flow rate adjustment device 75 is in the closed state, the process proceeds to step S110, and if the temperature difference Δ T is equal to or greater than the temperature difference threshold value Tth or the 2 nd flow rate adjustment device 75 is in the open state, the process proceeds to step S200. As described below, when the temperature difference Δ T is smaller than the temperature difference threshold value Tth and the 2 nd flow rate adjustment device 75 is in the closed state, the 1 st flow rate adjustment device 72 is the control target, and when the temperature difference Δ T is equal to or larger than the temperature difference threshold value Tth or the 2 nd flow rate adjustment device 75 is in the open state, the 2 nd flow rate adjustment device 75 is the control target.

In step S110, the control device 97 calculates a discharge temperature adjustment amount Δ Td, which is a value obtained by subtracting the target discharge temperature Tdn from the discharge temperature Td. The target discharge temperature Tdn is a preset value and is a value related to the specification of the compressor 10. The target discharge temperature Tdn is stored in a storage unit (not shown). In step S112, the control device 97 calculates the manipulated variable O1con, which is a value obtained by multiplying the discharge temperature adjustment amount Δ Td by the control constant G1. The control constant G1 is a value related to the control amount of the 1 st flow rate adjustment device 72, and is a positive value. The control constant G1 is set in advance and stored in a storage unit (not shown). Therefore, when the discharge temperature adjustment amount Δ Td is positive, that is, the discharge temperature is higher than the discharge temperature target value, the operation amount O1con of the 1 st flow rate adjustment device 72 is calculated in the opening direction. When the discharge temperature adjustment amount Δ Td is negative, that is, the discharge temperature is lower than the discharge temperature target value, the operation amount O1con of the 1 st flow rate adjustment device 72 is calculated in the off direction. In step S114, the control device 97 calculates the output opening O1n, which is a value obtained by adding the operation amount O1con to the current opening O1d of the 1 st flow rate adjustment device.

In step S116, control device 97 calculates a refrigerating machine oil superheat Osh, which is a value obtained by subtracting condensing temperature ET from refrigerating machine oil temperature Toil. In step 118, the control device 97 compares the refrigerator oil superheat Osh with the refrigerator oil superheat threshold OILsh. The refrigerator oil superheat threshold value OILsh is a preset value and is stored in a storage unit (not shown). The refrigerator oil superheat threshold value OILsh is, for example, 30K.

If the refrigerating machine oil superheat Osh is equal to or less than the refrigerating machine oil superheat threshold value OILsh in step S118, the process proceeds to step S120, and the control device 97 calculates a refrigerating machine oil superheat difference Δ Osh, which is a value obtained by subtracting the target refrigerating machine oil superheat value SHoil from the refrigerating machine oil superheat Osh. The target value SHoil of the degree of superheat of the refrigerating machine oil is a preset value and is stored in a storage unit (not shown). The target value SHoil of the degree of superheat of the refrigerating machine oil is, for example, 10K.

In step S122, the control device 97 calculates a refrigerating machine oil correction amount Δ oil which is a value obtained by multiplying the refrigerating machine oil superheat difference Δ Osh by the control constant G2. The control constant G2 is set to: the correction amount of the 1 st flow rate adjusting device 72 is always calculated in the closing direction when the refrigerator oil superheat degree difference Δ Osh of the refrigerator oil superheat degree Osh is positive, and the correction amount of the 1 st flow rate adjusting device 72 becomes larger as the refrigerator oil superheat degree difference Δ Osh becomes smaller, that is, as the refrigerator oil superheat degree Osh becomes closer to the target value of the refrigerator oil superheat degree Osh. In addition, the control constant G2 is set to: when the difference Δ Osh in the degree of superheat of the refrigerating machine oil Osh is negative, that is, the degree of superheat of the refrigerating machine oil Osh is lower than the target value of the degree of superheat of the refrigerating machine oil Osh, the correction amount of the 1 st flow rate adjusting device 72 is a fixed value.

In step S124, the controller 97 calculates a corrected opening O1op, which is a value obtained by adding the output opening O1nex to the refrigerating machine oil correction amount Δ oil, and proceeds to step S128.

When the refrigerator oil superheat Osh is greater than the refrigerator oil superheat threshold value OILsh in step S118, the process proceeds to step S126, and the controller 97 calculates the corrected opening O1op as the output opening Onex and proceeds to step S128.

In step S128, the control device 97 sets the opening degree of the 1 st flow rate adjustment device 72 to the correction opening degree O1 op.

In step S108, when the temperature difference Δ T is equal to or greater than the temperature difference threshold value Tth or the 2 nd flow rate adjustment device 75 is in the on state, the process proceeds to step S200.

In step S210 of fig. 10, the control device 97 calculates a discharge temperature adjustment amount Δ Td, which is a value obtained by subtracting the target discharge temperature Tdn from the discharge temperature Td. The target discharge temperature Tdn is a preset value and is a value related to the specification of the compressor 10. The target discharge temperature Tdn is stored in a storage unit (not shown). In step S212, the control device 97 calculates the manipulated variable O2con, which is a value obtained by multiplying the discharge temperature adjustment amount Δ Td by the control constant G3. The control constant G3 is a value related to the control amount of the 2 nd flow rate adjustment device 75, and is a positive value. The control constant G3 is set in advance and stored in a storage unit (not shown). Therefore, when the discharge temperature adjustment amount Δ Td is positive, that is, the discharge temperature is higher than the discharge temperature target value, the operation amount O2con of the 2 nd flow rate adjustment device 75 is calculated in the opening direction. When the discharge temperature adjustment amount Δ Td is negative, that is, the discharge temperature is lower than the discharge temperature target value, the operation amount O2con of the 2 nd flow rate adjustment device 75 is calculated in the off direction. In step S214, the control device 97 calculates an output opening O2n, which is a value obtained by adding the operation amount O2con to the current opening O2d of the 2 nd flow rate adjustment device.

In step S216, control device 97 calculates a refrigerating machine oil superheat Osh, which is a value obtained by subtracting condensing temperature ET from refrigerating machine oil temperature Toil. In step S218, the control device 97 compares the refrigerator oil superheat Osh with the refrigerator oil superheat threshold value OILsh. The refrigerator oil superheat threshold value OILsh is a preset value and is stored in a storage unit (not shown). The refrigerator oil superheat threshold value OILsh is, for example, 30K.

If the refrigerator oil superheat Osh is equal to or less than the refrigerator oil superheat threshold value OILsh in step S218, the process proceeds to step S220, and the controller 97 calculates a refrigerator oil superheat difference Δ Osh, which is a value obtained by subtracting the refrigerator oil superheat target value SHoil from the refrigerator oil superheat Osh. The target value SHoil of the degree of superheat of the refrigerating machine oil is a preset value and is stored in a storage unit (not shown). The target value SHoil of the degree of superheat of the refrigerating machine oil is, for example, 10K.

In step S222, the control device 97 calculates a refrigerating machine oil correction amount Δ oil which is a value obtained by multiplying the refrigerating machine oil superheat difference Δ Osh by the control constant G4. The control constant G4 is set to: the correction amount of the 2 nd flow rate adjusting device 75 is always calculated in the closing direction when the difference Δ Osh in the degree of superheat of the refrigerating machine oil Osh is positive, and the correction amount of the 2 nd flow rate adjusting device 75 becomes larger as the difference Δ Osh in the degree of superheat of the refrigerating machine oil becomes smaller, that is, as the degree of superheat of the refrigerating machine oil Osh becomes closer to the target value of the degree of superheat of the refrigerating machine oil Osh. In addition, the control constant G4 is set to: when the difference Δ Osh in the degree of superheat of the refrigerating machine oil Osh is negative, that is, the degree of superheat of the refrigerating machine oil Osh is lower than the target value of the degree of superheat of the refrigerating machine oil Osh, the correction amount of the 2 nd flow rate adjustment device 75 is a fixed value.

In step S224, the controller 97 calculates a corrected opening O2op, which is a value obtained by adding the output opening O2nex to the refrigerating machine oil correction amount Δ oii 2, and then proceeds to step S228.

When the refrigerator oil superheat Osh is greater than the refrigerator oil superheat threshold value OILsh in step S218, the process proceeds to step S226, and the controller 97 calculates the correction opening O2op as the output opening O2nex and proceeds to step S228.

In step S228, the control device 97 sets the opening degree of the 2 nd flow rate adjustment device 75 to the correction opening degree O2 op.

[ Effect of operation of the 1 st and 2 nd flow rate adjusting devices ]

In this way, the upper limit can be set for the amount of the refrigerating machine oil and the gas refrigerant bypassed from the oil separator 11 by making the opening degree necessary or not determined from the outlet temperature of the auxiliary heat exchanger 71, and therefore, it is possible to prevent excessive bypassing, and suppress a decrease in the capacity and a decrease in the performance.

Embodiment 4.

Fig. 11 is a diagram schematically illustrating an example of a circuit configuration of an air conditioning apparatus according to embodiment 4 of the present invention. In the air conditioner 103 of fig. 11, the same reference numerals are given to parts having the same configuration as the air conditioner 102 of fig. 8, and the description thereof is omitted. Compared to the air conditioner 102 of fig. 8, the air conditioner 103 of fig. 11 has the relay device 6.

The air conditioner 103 forms a 1 st-side cycle in which a 1 st refrigerant (hereinafter referred to as a refrigerant) flows between the outdoor unit 1 and the relay unit 6, forms a 2 nd-side cycle in which a heat medium (hereinafter referred to as a brine) flows between the relay unit 6 and the indoor units 2a to 2c, and performs heat exchange between the 1 st-side cycle and the 2 nd-side cycle in the 1 st intermediate heat exchanger 63a provided in the relay unit 6. As the coolant, water, an antifreeze, water added with an anticorrosive material, or the like can be used.

[ indoor machine ]

The plurality of indoor units 2a to 2c are, for example, indoor units having the same configuration, and each have a load side heat exchanger 21a to 21 c. The load side heat exchangers 21a to 21c are connected to the relay device 6 via branch pipes 4a to 4c, and exchange heat between the air supplied from the blowers of the fans 22a to 22c and the brine to generate heating air or cooling air to be supplied to the indoor space.

[ Relay device ]

The relay device 6 includes a 1 st flow rate control device 62a, a 1 st intermediate heat exchanger 63a, a 1 st pump 65a, and a plurality of 1 st flow path switching devices 66a to 66 c.

The 1 st flow rate control device 62a is constituted by a device whose opening degree can be variably controlled, such as an electronic expansion valve, and functions as a pressure reducing valve or an expansion valve that reduces pressure of the refrigerant and expands the refrigerant. The 1 st flow rate control device 62a is provided upstream of the 1 st intermediate heat exchanger 63a of the primary-side cycle in the flow of the refrigerant in the cooling operation mode.

The 1 st intermediate heat exchanger 63a is configured by, for example, a double-tube heat exchanger, a plate heat exchanger, or the like, and exchanges heat between the refrigerant circulating on the 1 st side and the refrigerant circulating on the 2 nd side. The 1 st intermediate heat exchanger 63a functions as an evaporator when the operating indoor unit performs cooling, and the 1 st intermediate heat exchanger 63a functions as a condenser when the operating indoor unit performs heating.

The 1 st pump 65a is constituted by, for example, an inverter type centrifugal pump or the like, and is in a state of being pressurized for sucking the brine. The 1 st pump 65a is provided upstream of the 1 st intermediate heat exchanger 63a in the secondary-side cycle.

The number of the 1 st flow path switching devices 66a to 66c is set to the number corresponding to the number of the indoor units 2a to 2c (3 in the example of fig. 11). The 1 st flow path switching devices 66a to 66c are configured by, for example, on-off valves, and open and close the flow paths from the 1 st intermediate heat exchanger 63a on the inflow side of the indoor units 2a to 2c, respectively. The 1 st flow path switching devices 66a to 66c are disposed downstream of the 1 st intermediate heat exchanger 63a in the secondary-side cycle.

In the relay device 6, an inlet temperature sensor 91a is provided at the inlet of the primary cycle of the 1 st intermediate heat exchanger 63a, and an outlet temperature sensor 92a is provided at the outlet of the primary cycle. The inlet temperature sensor 91a and the outlet temperature sensor 92a may be constituted by, for example, thermistors or the like.

In the relay device 6, an indoor unit outlet temperature sensor 93a is provided at the inlet of the secondary-side cycle of the 1 st intermediate heat exchanger 63a, and an indoor unit inlet temperature sensor 94a is provided at the outlet of the secondary-side cycle. The indoor unit outlet temperature sensor 93a and the indoor unit inlet temperature sensor 94a may be formed of, for example, thermistors.

As described above, the air conditioner 103 shown in fig. 11 can perform injection into the suction portion of the compressor 10 via the 1 st flow rate adjusting device 72 by cooling part of the refrigerating machine oil and the gas refrigerant separated in the oil separator 11, as in the air conditioner 100 shown in fig. 1 to 4.

Embodiment 5.

Fig. 12 is a diagram schematically illustrating an example of the circuit configuration of an air conditioning apparatus according to embodiment 5 of the present invention. Referring to fig. 12, an air conditioner 200 will be described. In fig. 12, the same reference numerals are given to parts having the same configuration as the air conditioner 100 of fig. 1, and the description thereof is omitted.

The air conditioner 200 of fig. 12 includes 1 outdoor unit 1 as a heat source unit, a plurality of indoor units 2a to 2c, and a relay unit 5 disposed between the outdoor unit 1 and the indoor units 2a to 2 c. The outdoor unit 1 and the relay device 5 are connected by a main pipe 3 through which a refrigerant flows, and the relay device 5 and the plurality of indoor units 2a to 2c are connected by branch pipes 4a to 4c through which the refrigerant flows. The cooling energy or the heating energy generated by the outdoor unit 1 is distributed to the indoor units 2a to 2c via the relay device 5.

The outdoor unit 1 and the relay unit 5 are connected by 2 main pipes 3, and the relay unit 5 and each indoor unit 2 are connected by 2 branch pipes 4a to 4 c. In this way, the outdoor unit 1 and the relay device 5, and the indoor units 2a to 2c and the relay device 5 are connected by 2 pipes, and the construction is easy.

[ outdoor machine ]

In the outdoor unit 1, the compressor 10, the oil separator 11, the refrigerant flow switching device 12, the heat source side heat exchanger 13, the accumulator 16, the 1 st bypass flow path 70, the auxiliary heat exchanger 71, and the 1 st flow rate adjusting device 72 are connected to each other, and mounted together with the fan 14 as a blower fan, as in the outdoor unit 1 of embodiment 1.

The outdoor unit 1 further includes a 1 st connecting pipe 18a, a 2

nd connecting pipe

18b, and 1 st backflow prevention devices 19a to 19d including check valves and the like. The 1 st backflow prevention device 19a prevents the high-temperature and high-pressure gas refrigerant from flowing backward from the 1 st connection pipe 18a to the heat source side heat exchanger 13 in the heating only operation mode and the heating main operation mode. The 1 st backflow prevention device 19b prevents the high-temperature and high-pressure gas refrigerant from flowing backward from the discharge-side flow path of the compressor 10 to the 2 nd connection pipe 18b in the heating only operation mode and the heating main operation mode. The 1 st backflow prevention device 19c prevents the high-pressure liquid or gas-liquid two-phase refrigerant from flowing backward from the 1 st connection pipe 18a to the accumulator 16 in the cooling only operation mode and the cooling main operation mode. The 1 st backflow prevention device 19d prevents the high-pressure liquid or gas-liquid two-phase refrigerant from flowing backward from the 1 st connection pipe 18a to the accumulator 16 in the cooling only operation mode and the cooling main operation mode.

By providing the 1 st connecting pipe 18a, the 2 nd connecting pipe 18b, and the 1 st backflow prevention devices 19a to 19d in this manner, the flow of the refrigerant flowing into the relay device 5 can be made constant regardless of the operation required by the indoor unit 2. The case where the 1 st backflow prevention devices 19a to 19d are configured by check valves is exemplified, but any configuration may be used as long as the backflow prevention devices can prevent the refrigerant from flowing backward, such as an opening and closing device or an expansion device having a fully-closed function.

[ indoor machine ]

The plurality of indoor units 2a to 2c are, for example, indoor units having the same configuration, and each have a load-side heat exchanger 21a to 21c and a load-side expansion device 20a to 20 c. The load side heat exchangers 21a to 21c are connected to the outdoor unit 1 via the branch pipes 4a to 4c, the relay device 5, and the main pipe 3, and generate heating air or cooling air to be supplied to the indoor space by performing heat exchange between the air supplied from the fans 22a to 22c and the refrigerant. The load-side expansion devices 20a to 20c are constituted by devices whose opening degree can be variably controlled, such as electronic expansion valves, and function as pressure reducing valves or expansion valves that reduce pressure and expand refrigerant. The load-side expansion devices 20a to 20c are provided on the upstream side of the load-side heat exchangers 21a to 21c in the flow of the refrigerant in the cooling only operation mode.

Further, the indoor unit 2 is provided with inlet-side temperature sensors 85a to 85c for detecting the temperature of the refrigerant flowing into the load-side heat exchanger 21, and outlet-side temperature sensors 84a to 84c for detecting the temperature of the refrigerant flowing out of the load-side heat exchanger 21. The inlet-side temperature sensors 85a to 85c and the outlet-side temperature sensors 84a to 84c are constituted by, for example, thermistors, and the detected inlet-side temperature and outlet-side temperature of the load-side heat exchangers 21a to 21c are sent to the control device 97.

In fig. 12, an example is shown in which 3 indoor units 2a to 2c are connected to the outdoor unit 1 via the relay device 5 and the refrigerant pipe 4, but the number of indoor units to be connected is not limited to 3, and may be 2 or more.

[ Relay device 5]

The relay device 5 includes a gas-liquid separator 50, a heat exchanger 52 related to refrigerant, a 3 rd throttling device 51, a 4 th throttling device 57, a plurality of 1 st switching devices 53a to 53c, a plurality of 2 nd switching devices 54a to 54c, a plurality of 2 nd backflow prevention devices 55a to 55c as backflow prevention devices such as check valves, and a plurality of 3 rd backflow prevention devices 56a to 56c as backflow prevention devices such as check valves.

In the cooling/heating hybrid operation mode with a large cooling load, the gas-liquid separator 50 separates the high-pressure refrigerant in a gas-liquid two-phase state generated in the outdoor unit 1 into liquid and gas, and causes the liquid to flow into the lower-side piping in fig. 12 to supply cooling energy to the indoor unit 2 and causes the gas to flow into the upper-side piping in fig. 12 to supply heating energy to the indoor unit 2. The gas-liquid separator 50 is provided at the inlet of the relay device 5.

The heat exchanger 52 related to refrigerant is configured by, for example, a double-tube heat exchanger or a plate heat exchanger, and exchanges heat between high-pressure or intermediate-pressure refrigerant and low-pressure refrigerant in order to sufficiently ensure the degree of supercooling of the refrigerant in a liquid or gas-liquid two-phase state supplied to the load-

side expansion devices

20a and 20b of the indoor unit 2 in which a cooling load occurs in the cooling only operation mode, the cooling main operation mode, and the heating main operation mode. The flow path of the refrigerant in a high-pressure or intermediate-pressure state in the heat exchanger related to refrigerant 52 is connected between the 3 rd expansion device 51 and the 2 nd backflow prevention devices 55a to 55 c. One end of the flow path of the refrigerant in the low-pressure state is connected between the 2 nd backflow prevention devices 55a to 55c and the outlet side of the flow path of the refrigerant in the high-pressure or intermediate-pressure state in the heat exchanger related to refrigerant 52, and the other end is conducted to the low-pressure pipe on the outlet side of the relay device 5 via the 4 th expansion device 57 and the heat exchanger related to refrigerant 52.

The 3 rd expansion device 51 has a function as a pressure reducing valve or an opening/closing valve, and reduces the pressure of the liquid refrigerant to a set pressure or opens and closes a flow path of the liquid refrigerant. The 3 rd expansion device 51 is composed of a device such as an electronic expansion valve whose opening degree can be variably controlled, and is provided in a pipe through which the liquid refrigerant flows out of the gas-liquid separator 50.

The 4 th expansion device 57 functions as a pressure reducing valve or an opening/closing valve, and opens and closes the refrigerant flow path in the heating only operation mode, and adjusts the bypass liquid flow rate in accordance with the indoor load in the heating main operation mode. The 4 th expansion device 57 is configured to adjust the degree of supercooling of the refrigerant supplied to the load-side expansion devices 20a to 20c of the indoor unit 2 in which the cooling load is generated by causing the refrigerant to flow out to the heat exchanger related to refrigerant 52 in the cooling only operation mode, the cooling main operation mode, and the heating main operation mode. The 4 th expansion device 57 is composed of a device whose opening degree can be variably controlled, such as an electronic expansion valve, and is provided in a flow path on the inlet side of the refrigerant in a low-pressure state in the heat exchanger related to refrigerant 52.

The number of the 1 st switching devices 53a to 53c is set to the number corresponding to the number of the indoor units 2a to 2c (3 in the example of fig. 12). The 2 nd switching devices 54a to 54c are configured by, for example, solenoid valves or the like, and switch the flow paths of the low-pressure and low-temperature gas refrigerant flowing out of the indoor units 2a to 2 c. The 1 st switching devices 53a to 53c are connected to a low-pressure pipe that conducts to the outlet side of the relay device 5. The 1 st opening/closing devices 53a to 53c may be throttle devices having a fully closing function as long as they can open and close the flow paths.

The 2 nd switching devices 54a to 54c are provided in a number (3 in the example of fig. 12) corresponding to the number of installed indoor units 2a to 2 c. The 2 nd switching devices 54a to 54c are configured by, for example, solenoid valves or the like, and open and close flow paths of the high-temperature and high-pressure gas refrigerant supplied to the indoor units 2a to 2c, respectively. The 2 nd opening/closing devices 54a to 54c are connected to the gas-side pipe of the gas-liquid separator 50, respectively. The 2 nd opening/closing devices 54a to 54c may be throttle devices having a fully closing function as long as the flow paths can be opened and closed.

The 2 nd backflow prevention devices 55a to 55c are provided in a number (3 in the example of fig. 12) corresponding to the number of installed indoor units 2a to 2 c. The plurality of 2 nd backflow prevention devices 55a to 55c cause the medium-temperature and medium-pressure liquid or gas-liquid two-phase refrigerant to flow out of the indoor units 2a to 2c that are performing the heating operation, and are connected to the pipe on the outlet side of the 3 rd expansion device 51. Thus, in the cooling main operation mode and the heating main operation mode, the refrigerant in the medium-temperature and medium-pressure liquid or gas-liquid two-phase state in which the supercooling degree cannot be sufficiently ensured, which has flowed out of the load-

side expansion devices

20a and 20b of the indoor unit 2 performing the heating operation, can be prevented from flowing into the load-

side expansion devices

20a and 20b of the indoor unit 2 performing the cooling operation. The 2 nd backflow prevention devices 55a to 55c are illustrated as check valves, but any device may be used as long as the backflow of the refrigerant can be prevented, and may be an opening/closing device or a throttle device having a fully closing function.

The 3 rd backflow prevention devices 56a to 56c are provided in a number (3 in the example of fig. 12) corresponding to the number of installed indoor units 2a to 2 c. The 3 rd backflow prevention devices 56a to 56c cause the high-pressure liquid refrigerant to flow into the indoor unit 2 that is performing the cooling operation, and are connected to the outlet pipe of the 3 rd throttling device 51. The 3 rd backflow prevention devices 56a to 56c prevent the medium-temperature and medium-pressure liquid or gas-liquid two-phase refrigerant, which has flowed out of the 3 rd expansion device 51 and cannot ensure a sufficient supercooling degree, from flowing into the load-side expansion device 20 of the indoor unit 2 that is performing the cooling operation, in the cooling main operation mode and in the heating main operation mode. The 3 rd backflow prevention devices 56a to 56c are illustrated as check valves or the like, but any device may be used as long as the backflow of the refrigerant can be prevented, and may be an opening and closing device or a throttle device having a fully closing function.

In the relay device 5, an inlet-side pressure sensor 86 is provided on the inlet side of the 3 rd throttle device 51, and an outlet-side pressure sensor 87 is provided on the outlet side of the 3 rd throttle device 51. The inlet side pressure sensor 86 detects the pressure of the high-pressure refrigerant, and the outlet side pressure sensor 87 detects the intermediate pressure of the liquid refrigerant discharged from the 3 rd throttling device 51 in the cooling main operation mode.

The relay device 5 is provided with a temperature sensor 88 for detecting the temperature of the refrigerant in a high-pressure or medium-pressure state flowing out of the heat exchanger related to refrigerant 52. The temperature sensor 88 is provided in a pipe on the outlet side of the flow path of the refrigerant in the high-pressure or medium-pressure state in the heat exchanger related to refrigerant 52, and may be constituted by a thermistor or the like.

The control device 97 controls the driving frequency of the compressor 10, the rotation speed (including on/off) of the fan 14, switching of the refrigerant flow path switching device 12, the opening degree of the 1 st flow rate adjusting device 72, the opening degrees of the load side throttling devices 20a to 20c, the 1 st switching devices 53a to 53c, the 2 nd switching devices 54a to 54c, the 3 rd throttling device 51, the 4 th throttling device 57, and the like based on the detection information of various sensors and instructions from the remote controller, and executes each operation mode described later. The control device 97 may be provided in at least 1 of the indoor units 2a to 2c, or may be provided in the relay device 5.

Next, each operation mode executed by the air conditioner 200 will be described. The present air conditioning apparatus 200 is capable of performing a cooling operation or a heating operation in the indoor unit that has received the instruction, among the indoor units 2a to 2 c. That is, the air conditioner 200 can perform the same operation in all the indoor units 2a to 2c, and can also perform different operations in each of the indoor units 2a to 2 c.

The operation modes executed by the air conditioner 200 include a cooling only operation mode, a cooling main operation mode, a heating only operation mode, and a heating main operation mode. The cooling only operation mode is a mode in which all the indoor units 2a to 2c perform cooling operation, the cooling main operation mode is a mode in which the indoor units 2a to 2c perform cooling/heating mixed operation and the cooling load is large, the heating only operation mode is a mode in which all the indoor units 2a to 2c perform heating operation, and the heating main operation mode is a mode in which the indoor units 2a to 2c perform cooling/heating mixed operation and the heating load is large. Hereinafter, each operation mode will be described.

[ full refrigeration operation mode ]

Fig. 13 is a diagram illustrating an example of the flow of the refrigerant in the cooling only operation mode of the air conditioning apparatus illustrated in fig. 12. In fig. 13, the flow path of the refrigerant cycle is indicated by a thick line, the flow direction of the refrigerant is indicated by a solid arrow, and the flow directions of the refrigerating machine oil and the refrigerant are indicated by a double arrow. In fig. 13, the cooling only operation mode will be described by taking as an example a case where cooling loads are generated in all of the load side heat exchangers 21a to 21 c. In the cooling only operation mode shown in fig. 13, the control device 97 switches the refrigerant flow switching device 12 so that the refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 13.

First, a low-temperature and low-pressure refrigerant is compressed by the compressor 10 to become a high-temperature and high-pressure gas refrigerant, and is discharged. The high-temperature high-pressure gas refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 13 via the oil separator 11 and the refrigerant flow switching device 12. Then, the refrigerant turns into a high-pressure liquid refrigerant while releasing heat to the outdoor air in the heat source side heat exchanger 13. The high-pressure liquid refrigerant flowing out of the heat source side heat exchanger 13 passes through the 1 st backflow prevention device 19a, flows out of the outdoor unit 1, passes through the main pipe 3, and flows into the relay device 5.

The high-pressure liquid refrigerant flowing into the relay device 5 is sufficiently supercooled in the heat exchanger 52 related to refrigerant via the gas-liquid separator 50 and the 3 rd expansion device 51. Most of the supercooled high-pressure refrigerant passes through the 2 nd backflow prevention devices 55a to 55c and the branch pipes 4a to 4c, and is expanded by the load-

side expansion devices

20a and 20b, thereby becoming a low-temperature low-pressure two-phase gas-liquid refrigerant. The remaining portion of the high-pressure refrigerant is expanded by the 4 th expansion device 57, and becomes a low-temperature low-pressure two-phase gas-liquid refrigerant. Then, the low-temperature low-pressure gas-liquid two-phase refrigerant exchanges heat with the high-pressure liquid refrigerant in the inter-refrigerant heat exchanger 52, becomes a low-temperature low-pressure gas refrigerant, and flows into the low-pressure piping on the outlet side of the relay device 5. At this time, the opening degree of the 4 th throttle device 57 is controlled such that: the degree of supercooling (subcool) obtained by using the difference between the saturation temperature converted from the pressure detected by the outlet-side pressure sensor 87 and the temperature detected by the temperature sensor 88 is made constant.

Most of the low-temperature low-pressure gas-liquid two-phase refrigerant flowing out of the load-side expansion devices 20a to 20c flows into the load-side heat exchangers 21a to 21c functioning as evaporators, and turns into a low-temperature low-pressure gas refrigerant while cooling the indoor air by absorbing heat from the indoor air. At this time, the opening degrees of the load-

side throttling devices

20a, 20b are controlled to: the degree of superheat (superheat) obtained by using the difference between the temperature detected by the inlet-side temperature sensor 85 and the temperature detected by the outlet-side temperature sensor 84 is made constant.

The gas refrigerant flowing out of each of the load side heat exchangers 21a to 21c merges with the gas refrigerant flowing out of the heat exchanger related to refrigerant 52 via the branch pipes 4a to 4c and the 1 st switching device 53, flows out of the relay device 5, passes through the main pipe 3, and flows into the outdoor unit 1 again. The refrigerant flowing into the outdoor unit 1 passes through the 1 st backflow prevention device 19b, passes through the refrigerant flow switching device 12 and the accumulator 16, and is again sucked into the compressor 10.

In the case where there is a load-side heat exchanger without a heat load, it is not necessary to flow the refrigerant to the load-side heat exchanger without a heat load, and therefore, the load-side expansion device connected to the load-side heat exchanger without a heat load is in an off state. When a heat load is generated from the load-side heat exchanger, the load-side expansion device connected to the load-side heat exchanger in which the heat load is generated may be opened to circulate the refrigerant. At this time, the opening degree of the load-side throttling device is controlled, for example, in the same manner as the load-side throttling devices 20a to 20c described above, such that: the degree of superheat (superheat) obtained by using the difference between the temperatures detected by the inlet-side temperature sensor 85 and the outlet-side temperature sensor 84 is made constant.

Next, the flow of the refrigerating machine oil is shown as follows. The refrigerating machine oil accumulated in the casing of the compressor 10 is heated by the refrigerant to a temperature equal to that of the refrigerant, and is discharged from the compressor 10. The high-temperature refrigerating machine oil discharged from the compressor 10 is separated by the oil separator 11, and flows into the auxiliary heat exchanger 71 through the 1 st bypass passage 70. The refrigerating machine oil flowing through the auxiliary heat exchanger 71 is cooled to the same temperature as the outdoor air supplied from the fan 14 while releasing heat to the outdoor air. The refrigerating machine oil flowing out of the auxiliary heat exchanger 71 is again sucked into the compressor 10 by the 1 st flow rate adjusting device 72.

[ refrigeration main operation mode ]

Fig. 14 is a diagram illustrating an example of the flow of the refrigerant in the cooling main operation mode of the air conditioning apparatus illustrated in fig. 12. In fig. 14, the cooling main operation mode will be described with respect to a case where a cooling load is generated in the load side heat exchangers 21a to 21b and a heating load is generated in the load side heat exchanger 21c as an example. In fig. 14, the flow path of the refrigerant cycle is indicated by a thick line, the flow direction of the refrigerant is indicated by a solid arrow, and the flow directions of the refrigerating machine oil and the refrigerant are indicated by a double arrow. In the cooling main operation mode shown in fig. 14, the controller 97 switches the refrigerant flow switching device 12 so that the heat-source-side refrigerant discharged from the compressor 10 flows into the heat-source-side heat exchanger 13.

First, a low-temperature and low-pressure refrigerant is compressed by the compressor 10 into a high-temperature and high-pressure gas refrigerant and discharged. The high-temperature high-pressure gas refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 13 via the oil separator 11 and the refrigerant flow switching device 12. Then, the refrigerant turns into a two-phase gas-liquid refrigerant while releasing heat to the outdoor air in the heat source side heat exchanger 13. The refrigerant flowing out of the heat source side heat exchanger 13 passes through the 1 st backflow prevention device 19a and the main pipe 3, and flows into the relay device 5.

The gas-liquid two-phase refrigerant flowing into the relay device 5 is separated into a high-pressure gas refrigerant and a high-pressure liquid refrigerant by the gas-liquid separator 50. The high-pressure gas refrigerant passes through the 2 nd switching device 54c and the branch tube 4c, flows into the load side heat exchanger 21c functioning as a condenser, and releases heat to the indoor air to heat the indoor space and turn into a liquid refrigerant. At this time, the opening degree of the load-side throttling device 20c is controlled to: the degree of supercooling (subcool) obtained by using the difference between the saturation temperature converted from the pressure detected by the inlet-side pressure sensor 86 and the temperature detected by the inlet-side temperature sensor 85c is made constant. The liquid refrigerant flowing out of the load side heat exchanger 21c is expanded by the load side expansion device 20c, and passes through the branch pipe 4c and the 2 nd backflow prevention device 55 c.

The liquid refrigerant having passed through the 2 nd backflow prevention device 55c merges with the intermediate-pressure liquid refrigerant that has been separated by the gas-liquid separator 50 and then expanded to the intermediate pressure in the 3 rd expansion device 51. At this time, the opening degree of the 3 rd throttle device 51 is controlled such that: the pressure difference between the pressure detected by the inlet-side pressure sensor 86 and the pressure detected by the outlet-side pressure sensor 87 is a predetermined pressure difference (for example, 0.3 MPa).

After the merged liquid refrigerant is sufficiently supercooled in the heat exchanger related to refrigerant 52, most of the merged liquid refrigerant passes through the 3 rd backflow prevention devices 56a to 56b and the branch pipes 4a to 4b, and is expanded by the load-side expansion devices 20a to 20b, thereby becoming a low-temperature, low-pressure, two-phase gas-liquid refrigerant. The remaining part of the liquid refrigerant is expanded by the 4 th expansion device 57, and becomes a low-temperature low-pressure gas-liquid two-phase refrigerant. At this time, the opening degree of the 4 th throttle device 57 is controlled such that: the degree of supercooling (subcool) obtained by using the difference between the saturation temperature converted from the pressure detected by the outlet-side pressure sensor 87 and the temperature detected by the temperature sensor 88 is made constant. Then, the low-temperature low-pressure gas-liquid two-phase refrigerant exchanges heat with the intermediate-pressure liquid refrigerant in the inter-refrigerant heat exchanger 52, becomes a low-temperature low-pressure gas refrigerant, and then flows into the low-pressure piping on the outlet side of the relay device 5.

On the other hand, the high-pressure liquid refrigerant separated in the gas-liquid separator 50 flows into the indoor units 2a to 2b via the heat exchanger 52 related to refrigerant and the 2 nd backflow prevention devices 55a to 55 b. Most of the refrigerant in the gas-liquid two-phase state expanded by the load-side expansion devices 20a to 20b of the indoor units 2a to 2b flows into the load-side heat exchangers 21a to 21b functioning as evaporators, and turns into a low-temperature low-pressure gas refrigerant while cooling the indoor air by absorbing heat from the indoor air. At this time, the opening degrees of the load-side throttling devices 20a to 20b are controlled to: the degrees of superheat (superheat) obtained by using the differences between the temperatures detected by the inlet-side temperature sensors 85a to 85b and the temperatures detected by the outlet-side temperature sensors 86a to 86b are made constant. The gas refrigerant flowing out of the load side heat exchangers 21a to 21b merges with the remaining part of the gas refrigerant flowing out of the heat exchanger related to refrigerant 52 via the branch pipes 4a to 4b and the 1 st switching devices 53a to 53b, flows out of the relay device 5, passes through the main pipe 3, and flows into the outdoor unit 1 again. The refrigerant flowing into the outdoor unit 1 passes through the 1 st backflow prevention device 19d, passes through the refrigerant flow switching device 12 and the accumulator 16, and is again sucked into the compressor 10.

In the case where there is a load-side heat exchanger without a heat load, it is not necessary to flow the refrigerant to the load-side heat exchanger without a heat load, and therefore, the load-side expansion device connected to the load-side heat exchanger without a heat load is in an off state. When a heat load is generated from the load-side heat exchanger, the load-side expansion device connected to the load-side heat exchanger in which the heat load is generated may be opened to circulate the refrigerant.

[ heating operation mode ]

Fig. 15 is a diagram illustrating an example of the flow of the refrigerant in the heating only operation mode of the air conditioning apparatus illustrated in fig. 12. In fig. 15, the flow path of the refrigerant cycle is indicated by a thick line, the flow direction of the refrigerant is indicated by a solid arrow, and the flow directions of the refrigerating machine oil and the refrigerant are indicated by a double arrow. In fig. 15, the heating only operation mode will be described by taking as an example a case where a heating load is generated in all of the load side heat exchangers 21a to 21 c. In the heating only operation mode shown in fig. 15, the controller 97 switches the refrigerant flow switching device 12 so that the heat-source-side refrigerant discharged from the compressor 10 flows into the relay device 5 without passing through the heat-source-side heat exchanger 13.

First, a low-temperature and low-pressure refrigerant is compressed by the compressor 10 into a high-temperature and high-pressure gas refrigerant and discharged. The high-temperature high-pressure gas refrigerant discharged from the compressor 10 passes through the oil separator 11, the refrigerant flow switching device 12, and the 1 st backflow prevention device 19c, and flows out of the outdoor unit 1. The high-temperature and high-pressure gas refrigerant flowing out of the outdoor unit 1 flows into the relay device 5 through the main pipe 3.

The high-temperature and high-pressure gas refrigerant flowing into the relay device 5 passes through the gas-liquid separator 50, the 2 nd opening/closing devices 54a to 54c, and the branch pipes 4a to 4c, and then flows into the load side heat exchangers 21a to 21c functioning as condensers. The refrigerant flowing into the load side heat exchangers 21a to 21c turns into a liquid refrigerant while heating the indoor space by releasing heat to the indoor air. The liquid refrigerant flowing out of the load side heat exchangers 21a to 21c is expanded by the load side expansion devices 20a to 20c, passes through the branch pipes 4a to 4c, the 2 nd backflow prevention devices 55a to 55c, the inter-refrigerant heat exchanger 52, the 4 th expansion device 57 controlled to be open, and the main pipe 3, and flows into the outdoor unit 1 again. At this time, the opening degrees of the load-side throttling devices 20a to 20c are controlled to: the degree of supercooling (subcool) obtained by using the difference between the value obtained by converting the pressure detected by the inlet-side pressure sensor 86 into the saturation temperature and the temperature detected by the inlet-side temperature sensors 85a to 85c is made constant.

The refrigerant flowing into the outdoor unit 1 passes through the 1 st backflow prevention device 19d, turns into a low-temperature low-pressure gas refrigerant while absorbing heat from the outdoor air in the heat source side heat exchanger 13, and is then sucked into the compressor 10 again via the refrigerant flow switching device 12 and the accumulator 16.

In the case where there is a load-side heat exchanger without a heat load, it is not necessary to flow the refrigerant to the load-side heat exchanger without a heat load, and therefore, the load-side expansion device connected to the load-side heat exchanger without a heat load is in an off state. When a heat load is generated from the load-side heat exchanger, the load-side expansion device connected to the load-side heat exchanger in which the heat load is generated may be opened to circulate the refrigerant. At this time, the opening degree of the load-side throttle device is controlled, for example, such that: the degree of supercooling (subcool) obtained by using the difference between the saturation temperature converted from the pressure detected by the inlet-side pressure sensor 86 and the temperature detected by the inlet-side temperature sensor 85 is made constant.

[ heating-main operation mode ]

Fig. 16 is a diagram illustrating an example of the flow of the refrigerant in the heating main operation mode of the air conditioning apparatus illustrated in fig. 12. In fig. 16, the flow path of the refrigerant cycle is indicated by a thick line, the flow direction of the refrigerant is indicated by a solid arrow, and the flow directions of the refrigerating machine oil and the refrigerant are indicated by a double arrow. In fig. 16, the heating-main operation mode will be described with respect to a case where a heating load is generated in the load-side heat exchangers 21a to 21b and a cooling load is generated in the load-side heat exchanger 21c as an example. In the heating-main operation mode shown in fig. 16, the controller 97 switches the refrigerant flow switching device 12 so that the heat-source-side refrigerant discharged from the compressor 10 flows into the relay device 5 without passing through the heat-source-side heat exchanger 13.

The high-temperature and high-pressure gas refrigerant flowing into the relay device 5 passes through the gas-liquid separator 50, the 2 nd opening/closing devices 54a to 54b, and the branch pipes 4a to 4b, and then flows into the load side heat exchangers 21a to 21b functioning as condensers. The refrigerant flowing into the load side heat exchangers 21a to 21b turns into a liquid refrigerant while heating the indoor space by releasing heat to the indoor air. The liquid refrigerant flowing out of the load side heat exchangers 21a to 21b is expanded by the load side expansion devices 20a to 20b, and is sufficiently cooled in the inter-refrigerant heat exchanger 52 via the branch pipes 4a to 4b and the 2 nd backflow prevention devices 55a to 55 b. Most of the refrigerant passes through the 3 rd backflow prevention device 56c and the branch pipe 4c, is expanded by the load-side expansion device 20c, and is a low-temperature, low-pressure, two-phase gas-liquid refrigerant. The remaining part of the liquid refrigerant is expanded by the 4 th expansion device 57 also used as a bypass, and becomes a low-temperature low-pressure gas-liquid two-phase refrigerant, and the low-temperature low-pressure gas-liquid two-phase refrigerant flows into the low-pressure piping on the outlet side of the relay device 5 by exchanging heat with the liquid refrigerant in the inter-refrigerant heat exchanger 52.

Most of the refrigerant in the gas-liquid two-phase state expanded by the load-side expansion device 20c flows into the load-side heat exchanger 21c functioning as an evaporator, and absorbs heat from the indoor air to cool the indoor air and turn into the refrigerant in the gas-liquid two-phase state of low temperature and medium pressure. The two-phase gas-liquid refrigerant flowing out of the load side heat exchanger 21c merges with the remaining portion of the refrigerant flowing out of the heat exchanger related to refrigerant 52 via the branch pipe 4c and the 1 st switching device 53c, flows out of the relay device 5, passes through the main pipe 3, and flows into the outdoor unit 1 again. The refrigerant flowing into the outdoor unit 1 passes through the 1 st backflow prevention device 19d, becomes a low-temperature low-pressure gas-liquid two-phase refrigerant, turns into a low-temperature low-pressure gas refrigerant while absorbing heat from outdoor air in the heat source side heat exchanger 13, and is again sucked into the compressor 10 via the refrigerant flow switching device 12 and the accumulator 16.

At this time, the opening degrees of the load-side throttling devices 20a to 20b are controlled to: the degree of supercooling (subcool) obtained as the difference between the value obtained by converting the pressure detected by the inlet-side pressure sensor into the saturation temperature and the temperature detected by the inlet-side temperature sensors 85a to 85b is made constant. On the other hand, the opening degree of the load-side throttling device 20c is controlled such that: the degree of superheat (superheat) obtained by using the difference between the temperature detected by the inlet-side temperature sensor 85c and the temperature detected by the outlet-side temperature sensor 84c is made constant.

Further, the opening degree of the 4 th throttle device 57 is controlled such that: the degree of supercooling (subcool) obtained by using the difference between the saturation temperature converted from the pressure detected by the outlet-side pressure sensor 87 and the temperature detected by the temperature sensor 88 is made constant.

As described above, in the air conditioning apparatus 200 shown in fig. 12 to 16, in the cooling only operation mode, the cooling main operation mode, the heating only operation mode, and the heating main operation mode, as in the air conditioning apparatus 100 shown in fig. 1 to 4, by cooling part of the refrigerating machine oil and the gas refrigerant separated in the oil separator 11, injection into the suction portion of the compressor 10 can be performed via the 1 st flow rate adjusting device 72.

Embodiment 6.

Fig. 17 is a diagram schematically illustrating an example of the circuit configuration of an air conditioner according to embodiment 6 of the present invention. In the air conditioner 201 of fig. 17, the same reference numerals are given to parts having the same configuration as the air conditioner 200 of fig. 12, and the description thereof is omitted. In the air conditioner 201 of fig. 17, the outdoor unit 1 has a different configuration from the air conditioner 200 of fig. 12. That is, the outdoor unit 1 of the example of the present embodiment further includes a flow rate adjuster 73 arranged in parallel with the 1 st flow rate adjuster 72. The flow rate adjuster 73 is constituted by a device such as a capillary tube to which a flow path resistance value is fixed.

In the air conditioner 201, for example, when the discharge temperature of the compressor 10 detected by the discharge temperature sensor 80 is equal to or lower than the discharge temperature threshold, the controller 97 controls the 1 st flow rate adjusting device 72 so that the 1 st flow rate adjusting device 72 is in the fully-closed state. The discharge temperature threshold value is, for example, a temperature lower than a temperature at which the compressor 10 is at risk of damage or a temperature at which the refrigerator oil is at risk of degradation, and is set to, for example, 115 degrees or less. The discharge temperature threshold value is set in advance in accordance with a limit value of the discharge temperature of the compressor 10 or the like, and is stored in, for example, a storage unit (not shown).

As described above, since the outdoor unit 1 of the present embodiment includes the flow rate adjuster 73 disposed in parallel with the 1 st flow rate adjuster 72, even when the 1 st flow rate adjuster 72 is in an abnormal state and is in a closed state, the refrigerating machine oil or the refrigerating machine oil and the refrigerant circulate in the order of the compressor 10, the oil separator 11, the auxiliary heat exchanger 71, the flow rate adjuster 73, and the compressor 10. Therefore, even when the 1 st flow rate adjustment device 72 is in the closed state due to an abnormality, the refrigerating machine oil in an amount not short of the refrigerating machine oil in the compressor 10 flows into the suction portion of the compressor 10 through the auxiliary heat exchanger 71 and the flow rate adjuster 73. Therefore, according to the outdoor unit 1 of the example of the present embodiment, even when the 1 st flow rate adjustment device 72 is in the closed state due to an abnormality, it is possible to secure the amount of the refrigerating machine oil necessary for lubrication and sealing of the compressor 10 while suppressing an increase in the discharge temperature of the compressor 10. Therefore, according to the outdoor unit 1 of the example of the present embodiment, the risk of damage to the compressor 10 can be reliably suppressed.

Embodiment 7.

Fig. 18 is a diagram schematically illustrating an example of the circuit configuration of an air conditioning apparatus according to embodiment 7 of the present invention. In the air conditioner 202 of fig. 18, the same reference numerals are given to parts having the same configuration as the air conditioner 201 of fig. 17, and the description thereof is omitted. In the air conditioner 202 of fig. 18, the outdoor unit 1 is different in configuration from the air conditioner 201 of fig. 17. That is, the outdoor unit 1 of the present embodiment further includes the 2 nd bypass flow path 74 in which the 2 nd flow rate adjusting device 75 is disposed. One end of the 2 nd bypass passage 74 is connected to a pipe between the heat source side heat exchanger 13 and the main pipe 3 through which the liquid refrigerant flows in any of the cooling only operation mode, the cooling main operation mode, the heating only operation mode, and the heating main operation mode, and the other end is connected to the outflow side of the 1 st flow control device 72. That is, the 2 nd bypass passage 74 bypasses the pipe connecting the heat source side heat exchanger 13 and the load

side expansion devices

side throttling devices

The pressure adjusting device 76 is fully opened in the cooling only operation mode and the cooling main operation mode, for example. The pressure adjusting device 76 is set to an opening degree that increases the pressure from the outlet of the load-side expansion devices 20a to 20c of the indoor unit 2 to the inlet of the pressure adjusting device 76 to an intermediate pressure in the heating only operation mode and the heating main operation mode, for example. That is, the pressure adjusting device 76 is controlled to: the value detected by the medium pressure detection sensor 77 is set to a preset pressure value.

As described above, in the air-conditioning apparatus 202 of the example of the present embodiment, in any of the cooling only operation mode, the cooling main operation mode, the heating only operation mode, and the heating main operation mode, the suction enthalpy of the compressor 10 can be reduced by the fluid cooled by the auxiliary heat exchanger 71, and the suction enthalpy of the compressor 10 can be reduced by a part of the refrigerant cooled by the heat source side heat exchanger 13. Therefore, according to the air conditioner 202 of the example of the present embodiment, when the discharge temperature of the compressor 10 increases, the increase in the discharge temperature of the compressor 10 can be suppressed. That is, for example, even when the heat exchange capacity, which is the processing capacity of the auxiliary heat exchanger 71, reaches the upper limit, the 2 nd flow rate adjustment device 75 can be turned on to suppress the increase in the discharge temperature of the compressor 10. According to the air conditioner 202 of the example of the present embodiment, since an increase in the discharge temperature of the compressor 10 can be suppressed, degradation of the refrigerating machine oil and damage to the compressor 10 can be suppressed. Further, since the refrigerating machine oil in the suction portion of the compressor 10 can be reliably cooled, the loss due to the suction heating of the compressor 10 can be suppressed. Furthermore, since the increase in the discharge temperature of the compressor 10 is suppressed, the rotational speed of the compressor 10 can be increased, and the intensity of cooling can be increased.

Embodiment 8.

Fig. 19 is a diagram schematically illustrating an example of the circuit configuration of an air conditioning apparatus according to embodiment 8 of the present invention. In the air conditioner 300 of fig. 19, the same reference numerals are given to parts having the same configuration as the air conditioner 200 of fig. 12, and the description thereof is omitted. In air conditioner 300 in fig. 19, relay device 6 has a different configuration from air conditioner 200 in fig. 12.

The air conditioning apparatus 300 forms a 1 st-side cycle in which a 1 st refrigerant (hereinafter referred to as a refrigerant) flows between the outdoor unit 1 and the relay unit 6, forms a 2 nd-side cycle in which a heat medium (hereinafter referred to as a brine) flows between the relay unit 6 and the indoor units 2a to 2c, and performs heat exchange between the 1 st-side cycle and the 2 nd-side cycle in the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b provided in the relay unit 6. As the coolant, water, an antifreeze, water added with an anticorrosive material, or the like can be used.

[ indoor machine ]

The plurality of indoor units 2a to 2c are, for example, indoor units having the same configuration, and each have a load side heat exchanger 21a to 21 c. The load side heat exchangers 21a to 21c are connected to the relay device 6 via branch pipes 4a to 4c, and exchange heat between the air supplied from the blowers of the fans 22a to 22c and the coolant to generate heating air or cooling air to be supplied to the indoor space.

[ Relay device ]

The relay device 6 includes the heat exchanger related to refrigerant 60, the 3 rd throttle device 61, the 4 th throttle device 68, the 1 st flow rate control device 62a, the 2 nd flow rate control device 62b, the 1 st intermediate heat exchanger 63a, the 2 nd intermediate heat exchanger 63b, the 1 st flow path switching device 64a, the 2 nd flow path switching device 64b, the 1 st pump 65a, the 2 nd pump 65b, a plurality of the 1 st flow path switching devices 66a to 66c, and a plurality of the 2 nd flow path switching devices 67a to 67 c.

The 1 st flow rate control device 62a and the 2 nd flow rate control device 62b are constituted by devices whose opening degrees can be variably controlled, such as electronic expansion valves, and function as a pressure reducing valve or an expansion valve that reduces pressure of the refrigerant and expands the refrigerant. The 1 st flow rate control device 62a and the 2 nd flow rate control device 62b are provided upstream of the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b of the primary cycle in the flow of the refrigerant in the cooling only operation mode.

The 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b are constituted by, for example, a double-tube heat exchanger, a plate heat exchanger, or the like, and exchange heat between the refrigerant circulating on the 1 st side and the refrigerant circulating on the 2 nd side. When both of the operating indoor units perform cooling, the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b function as evaporators, when both of the operating indoor units perform heating, the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b function as condensers, and when both of the operating indoor units perform cooling and heating, one of the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b functions as a condenser and the other one functions as an evaporator.

The 1 st flow path switching device 64a and the 2 nd flow path switching device 64b are configured by, for example, a four-way valve or the like, and switch the refrigerant flow paths in the cooling only operation mode, the cooling main operation mode, the heating only operation mode, and the heating main operation mode. In the cooling only operation mode, both the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b function as evaporators. In the cooling-main operation mode and the heating-main operation mode, for example, the 1 st intermediate heat exchanger 63a functions as an evaporator, and the 2 nd intermediate heat exchanger 63b functions as a condenser. In the heating only operation mode, both the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b function as condensers. The 1 st flow switching device 64a and the 2 nd flow switching device 64b are provided downstream of the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b of the primary-side cycle in the flow of the refrigerant in the cooling only operation mode.

The 1 st pump 65a and the 2 nd pump 65b are formed of, for example, inverter type centrifugal pumps or the like, and are in a state of being pressurized for sucking the brine. The 1 st pump 65a and the 2 nd pump 65b are provided upstream of the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b in the secondary-side cycle.

The number of the 1 st flow path switching devices 66a to 66c is set to the number corresponding to the number of the indoor units 2a to 2c (3 in the example of fig. 19). The 1 st flow path switching devices 66a to 66c are configured by, for example, two-way valves or the like, and switch the connection destination on the inflow side of each of the indoor units 2a to 2c to the flow path from the 1 st intermediate heat exchanger 63a and the flow path from the 2 nd intermediate heat exchanger 63b, respectively. The 1 st flow path switching devices 66a to 66c are provided downstream of the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b in the secondary-side cycle.

The plurality of 2 nd flow path switching devices 67a to 67c are provided in a number (3 in the example of fig. 19) corresponding to the number of installed indoor units 2a to 2 c. The plurality of 2 nd flow path switching devices 67a to 67c are configured by, for example, two-way valves or the like, and switch the connection destination on the outflow side of each of the indoor units 2a to 2c to the flow path to the 1 st pump 65a and the flow path to the 2 nd pump 65b, respectively. The 2 nd flow path switching devices 67a to 67c are provided upstream of the 1 st pump 65a and the 2 nd pump 65b in the secondary-side cycle.

In the relay device 6, an inlet temperature sensor 89 is provided at an inlet on the low-pressure side of the heat exchanger related to refrigerant 60, and an outlet temperature sensor 90 is provided at an outlet on the low-pressure side of the heat exchanger related to refrigerant 60. The inlet temperature sensor 89 and the outlet temperature sensor 90 may be constituted by, for example, thermistors or the like.

In the relay device 6, inlet temperature sensors 91a to 91b are provided at inlets of the primary-side cycles of the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b, and outlet temperature sensors 92a to 92b are provided at outlets of the primary-side cycles. The inlet temperature sensors 91a to 91b and the outlet temperature sensors 92a to 92b may be configured by thermistors or the like, for example.

In the relay device 6, indoor unit outlet temperature sensors 93a to 93b are provided at inlets of the secondary-side cycle of the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b, indoor unit inlet temperature sensors 94a to 94b are provided at outlets of the secondary-side cycle, and indoor unit outlet temperature sensors 95a to 95d are provided at inlets of the plurality of 2 nd flow path switching devices 67a to 67 c. The indoor unit outlet temperature sensors 93a to 93b, the indoor unit inlet temperature sensors 94a to 94b, and the indoor unit outlet temperature sensors 95a to 95d may be configured by, for example, thermistors.

In the relay device 6, an outlet pressure sensor 98 is provided on the outlet side of the 2 nd intermediate heat exchanger 63 b. The outlet pressure sensor 98 detects the pressure of the high-pressure refrigerant.

[ full refrigeration operation mode ]

Fig. 20 is a diagram illustrating an example of the operation of the air conditioning apparatus shown in fig. 19 in the cooling only operation mode. In fig. 20, the flow path of the refrigerant cycle is indicated by a thick line, the flow direction of the refrigerant is indicated by a solid line arrow, the flow directions of the refrigerating machine oil and the refrigerant are indicated by a double line arrow, and the flow direction of the brine is indicated by a broken line arrow. In the cooling only operation mode, the controller 97 switches the refrigerant flow switching device 12 so that the refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 13.

First, the operation of the primary-side cycle in the cooling only operation mode will be described. The high-pressure liquid refrigerant flowing into the relay device 6 passes through the 3 rd expansion device 61 controlled to be in an open state after being sufficiently supercooled in the inter-refrigerant heat exchanger 60. Most of the supercooled high-pressure refrigerant is expanded by the 1 st flow rate control device 62a and the 2 nd flow rate control device 62b, and becomes a low-temperature low-pressure gas-liquid two-phase refrigerant. The remaining portion of the high-pressure refrigerant is expanded by the 4 th expansion device 68, and becomes a low-temperature low-pressure two-phase gas-liquid refrigerant. Then, the low-temperature low-pressure gas-liquid two-phase refrigerant expanded by the 4 th expansion device 68 exchanges heat with the high-pressure liquid refrigerant in the inter-refrigerant heat exchanger 60, becomes a low-temperature low-pressure gas refrigerant, and then flows into the low-pressure piping on the outlet side of the relay device 6. At this time, the opening degree of the 4 th throttle device 68 is controlled such that: the degree of superheat (superheat) obtained by using the difference between the temperature detected by the inlet temperature sensor 89 and the temperature detected by the outlet temperature sensor 90 is made constant.

Most of the low-temperature low-pressure gas-liquid two-phase refrigerant flowing out of the 1 st flow control device 62a and the 2 nd flow control device 62b flows into the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b functioning as evaporators, and turns into a low-temperature low-pressure gas refrigerant while cooling the brine. At this time, the opening degrees of the 1 st flow rate control device 62a and the 2 nd flow rate control device 62b are controlled such that: the degrees of superheat (superheat) obtained by using the differences between the temperatures detected by the inlet temperature sensors 91a to 91b and the temperatures detected by the outlet temperature sensors 92a to 92b are made constant.

The gas refrigerant flowing out of each of the 1 st and 2 nd

intermediate heat exchangers

63a and 63b merges with the gas refrigerant flowing out of the heat exchanger related to refrigerant 60 via the 1 st and 2 nd

flow switching devices

64a and 64b, flows out of the relay device 6, passes through the main pipe 3, and flows into the outdoor unit 1. The refrigerant flowing into the outdoor unit 1 passes through the 1 st backflow prevention device 19b, passes through the refrigerant flow switching device 12 and the accumulator 16, and is again sucked into the compressor 10.

Next, the operation of the secondary side cycle in the cooling only operation mode will be described. The coolant pressurized by the 1 st pump 65a and the 2 nd pump 65b flows into the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63 b. The coolant having a low temperature in the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b passes through the 1 st flow switching devices 66a to 66c set in a state of communicating with both or either one of the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b, and flows into the load side heat exchangers 21a to 21 c. The coolant flowing through the load side heat exchangers 21a to 21c cools the air in the room to perform cooling. During cooling, the coolant is heated by the indoor air and returns to the 1 st pump 65a and the 2 nd pump 65b in the relay device 6 through the 2 nd flow path switching devices 67a to 67 c. At this time, the voltages of the 1 st pump 65a and the 2 nd pump 65b are controlled to: for example, the difference between the temperature detected by the indoor unit inlet temperature sensors 94a to 94b and the temperature detected by the indoor unit outlet temperature sensors 93a to 93b is made constant.

[ refrigeration main operation mode ]

Fig. 21 is a diagram illustrating an example of an operation in the cooling main operation mode of the air conditioner illustrated in fig. 19. In fig. 21, the flow path of the refrigerant cycle is indicated by a thick line, the flow direction of the refrigerant is indicated by a solid line arrow, the flow directions of the refrigerating machine oil and the refrigerant are indicated by a double line arrow, and the flow direction of the brine is indicated by a broken line arrow. In the cooling main operation mode, the control device 97 switches the refrigerant flow switching device 12 so that the refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 13.

First, the operation of the primary-side cycle in the cooling main operation mode will be described. The two-phase gas-liquid refrigerant flowing into the relay device 6 is separated into a high-pressure gas refrigerant and a high-pressure liquid refrigerant on the upstream side of the inter-refrigerant heat exchanger 60. The high-pressure gas refrigerant flows into the 2 nd intermediate heat exchanger 63b functioning as a condenser after passing through the 2 nd flow switching device 64b, and turns into a liquid refrigerant while heating the brine. At this time, the opening degree of the 2 nd flow rate control device 62b is controlled to: the degree of supercooling (subcool) obtained by using the difference between the saturation temperature converted from the pressure detected by the outlet pressure sensor 98 and the temperature detected by the inlet temperature sensor 91b is made constant. The liquid refrigerant flowing out of the 2 nd intermediate heat exchanger 63b is expanded by the 2 nd flow control device 62 b.

The high-pressure liquid refrigerant separated on the upstream side of the heat exchanger related to refrigerant 60 passes through the heat exchanger related to refrigerant 60, and is expanded to an intermediate pressure by the 3 rd expansion device 61 to become an intermediate-pressure liquid refrigerant. The intermediate-pressure liquid refrigerant expanded by the 3 rd expansion device 61 merges with the liquid refrigerant expanded by the 2 nd flow control device 62 b.

Most of the merged liquid refrigerant is expanded by the 1 st flow rate control device 62a, and becomes a low-temperature low-pressure two-phase gas-liquid refrigerant. The remaining part of the merged liquid refrigerant is expanded by the 4 th expansion device 68, and becomes a low-temperature low-pressure gas-liquid two-phase refrigerant. At this time, the opening degree of the 4 th throttle device 68 is controlled such that: the degree of superheat (superheat) obtained by using the difference between the temperature detected by the inlet temperature sensor 89 and the temperature detected by the outlet temperature sensor 90 is made constant. Then, the low-temperature low-pressure gas-liquid two-phase refrigerant exchanges heat with the high-pressure liquid refrigerant in the inter-refrigerant heat exchanger 60, becomes a low-temperature low-pressure gas refrigerant, and flows into the low-pressure piping on the outlet side of the relay device 6.

Most of the gas-liquid two-phase refrigerant expanded by the 1 st flow control device 62a flows into the 1 st intermediate heat exchanger 63a functioning as an evaporator, and turns into a low-temperature low-pressure gas refrigerant while cooling the brine. At this time, the opening degree of the 1 st flow rate control device 62a is controlled to: the degree of superheat (superheat) obtained by using the difference between the temperature detected by the inlet temperature sensor 91a and the temperature detected by the outlet temperature sensor 92a is made constant. The gas refrigerant flowing out of the 1 st intermediate heat exchanger 63a merges with the remaining part of the gas refrigerant flowing out of the heat exchanger related to refrigerant 60 via the 1 st flow switching device 64a, flows out of the relay device 6, passes through the main pipe 3, and flows into the outdoor unit 1 again. The refrigerant flowing into the outdoor unit 1 passes through the 1 st backflow prevention device 19b, passes through the refrigerant flow switching device 12 and the accumulator 16, and is again sucked into the compressor 10.

Next, the operation of the secondary side cycle in the cooling main operation mode will be described. In the secondary-side cycle, for example, the indoor units 2a to 2b perform a cooling operation, and the indoor unit 2c performs a heating operation. First, the indoor units 2a to 2b that perform cooling operation in the cooling main operation mode will be described. The coolant pressurized by the 1 st pump 65a flows into the 1 st intermediate heat exchanger 63 a. The coolant having a low temperature in the 1 st intermediate heat exchanger 63a passes through the 1 st flow switching devices 66a to 66b set in a state of being communicated with the 1 st intermediate heat exchanger 63a, and flows into the load side heat exchangers 21a to 21 b. The coolant flowing through the load side heat exchangers 21a to 21b cools the air in the room to perform cooling. During cooling, the coolant is heated by the indoor air and returns to the 1 st pump 65a in the relay device 6 through the 2 nd flow switching devices 67a to 67 b. At this time, the voltage of the 1 st pump 65a is controlled to: for example, the difference between the temperature detected by the indoor unit inlet temperature sensor 94a and the temperature detected by the indoor unit outlet temperature sensor 93a is made constant.

Next, a description will be given of the indoor unit 2c that performs the heating operation in the cooling main operation mode. The coolant pressurized by the 2 nd pump 65b flows into the 2 nd intermediate heat exchanger 63 b. The coolant having a high temperature in the 2 nd intermediate heat exchanger 63b passes through the 1 st flow switching device 66c set in a state of being communicated with the 2 nd intermediate heat exchanger 63b, and flows into the load side heat exchanger 21 c. The coolant flowing through the load side heat exchanger 21c heats the indoor air and performs heating. During heating, the coolant is cooled by the indoor air and returned to the 2 nd pump 65b in the relay device 6 through the 2 nd flow switching device 67 c. At this time, the voltage of the 2 nd pump 65b is controlled to: for example, the difference between the temperature detected by the indoor unit inlet temperature sensor 94b and the temperature detected by the indoor unit outlet temperature sensor 93b is made constant.

[ heating operation mode ]

Fig. 22 is a diagram illustrating an example of an operation in the heating only operation mode of the air conditioner illustrated in fig. 19. In fig. 22, the flow path of the refrigerant cycle is indicated by a thick line, the flow direction of the refrigerant is indicated by a solid line arrow, the flow directions of the refrigerating machine oil and the refrigerant are indicated by a double line arrow, and the flow direction of the brine is indicated by a broken line arrow. In the heating only operation mode, the controller 97 switches the refrigerant flow switching device 12 so that the heat-source-side refrigerant discharged from the compressor 10 flows into the relay device 6 without passing through the heat-source-side heat exchanger 13.

First, the operation of the primary cycle in the heating only operation mode will be described. The high-temperature and high-pressure gas refrigerant flowing into the relay device 6 passes through the 1 st flow switching device 64a and the 2 nd flow switching device 64b and flows into the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b functioning as condensers, respectively. The refrigerant flowing into the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b turns into a liquid refrigerant while heating the brine. The liquid refrigerant flowing out of the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b is expanded by the 1 st flow rate control device 62a and the 2 nd flow rate control device 62b, passes through the 4 th expansion device 68 and the main pipe 3, which are controlled to be opened, and flows into the outdoor unit 1 again. At this time, the opening degrees of the 1 st flow rate control device 62a and the 2 nd flow rate control device 62b are controlled such that: the degree of supercooling (subcool) obtained by using the difference between the value obtained by converting the pressure detected by the outlet pressure sensor 98 into the saturation temperature and the temperature detected by the inlet temperature sensors 91a to 91b is made constant.

Next, the operation of the secondary side cycle in the heating only operation mode will be described. The coolant pressurized by the 1 st pump 65a and the 2 nd pump 65b flows into the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63 b. The coolant having a high temperature in the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b passes through the 1 st flow switching devices 66a to 66c set in a state of communicating with both or either of the 1 st intermediate heat exchanger 63a and the 2 nd intermediate heat exchanger 63b, and flows into the load side heat exchangers 21a to 21 c. The coolant flowing through the load side heat exchangers 21a to 21c heats the indoor air and heats the air. During heating, the coolant is cooled by the indoor air and returns to the 1 st pump 65a and the 2 nd pump 65b in the relay device 6 through the 2 nd flow path switching devices 67a to 67 c. At this time, the voltages of the 1 st pump 65a and the 2 nd pump 65b are controlled to: for example, the difference between the temperature detected by the indoor unit inlet temperature sensors 94a to 94b and the temperature detected by the indoor unit outlet temperature sensors 93a to 93b is made constant.

Next, the flow of the refrigerating machine oil is shown as follows. The refrigerating machine oil accumulated in the casing of the compressor 10 is heated by the refrigerant to a temperature equal to that of the refrigerant, and is discharged from the compressor 10. The high-temperature refrigerating machine oil discharged from the compressor 10 is separated by the oil separator 11, and flows into the auxiliary heat exchanger 71 through the 1 st bypass passage 70. Then, the refrigerating machine oil flowing through the auxiliary heat exchanger 71 is cooled to the same temperature as the outdoor air while releasing heat to the outdoor air supplied from the fan 14. The refrigerating machine oil flowing out of the auxiliary heat exchanger 71 is again sucked into the compressor 10 by the 1 st flow rate adjusting device 72.

[ heating-main operation mode ]

Fig. 23 is a diagram illustrating an example of an operation in the heating main operation mode of the air conditioning apparatus illustrated in fig. 19. In fig. 23, the flow path of the refrigerant cycle is indicated by a thick line, the flow direction of the refrigerant is indicated by a solid line arrow, the flow directions of the refrigerating machine oil and the refrigerant are indicated by a double line arrow, and the flow direction of the brine is indicated by a broken line arrow. In fig. 23, the heating-main operation mode will be described by taking as an example a case where a heating load is generated in the load-side heat exchangers 21a to 21b and a cooling load is generated in the load-side heat exchanger 21 c. In the heating-main operation mode shown in fig. 23, the controller 97 switches the refrigerant flow switching device 12 so that the heat-source-side refrigerant discharged from the compressor 10 flows into the relay device 6 without passing through the heat-source-side heat exchanger 13.

First, the operation of the primary-side cycle in the heating-main operation mode will be described. The high-temperature and high-pressure gas refrigerant that has flowed into the relay device 6 is separated into a high-pressure gas refrigerant and a high-pressure liquid refrigerant on the upstream side of the inter-refrigerant heat exchanger 60. The high-pressure gas refrigerant flows into the 2 nd intermediate heat exchanger 63b functioning as a condenser after passing through the 2 nd flow switching device 64b, and turns into a liquid refrigerant while heating the brine. At this time, the opening degree of the 2 nd flow rate control device 62b is controlled to: the degree of supercooling (subcool) obtained by using the difference between the saturation temperature converted from the pressure detected by the outlet pressure sensor 98 and the temperature detected by the inlet temperature sensor 91b is made constant. The liquid refrigerant flowing out of the 2 nd intermediate heat exchanger 63b is expanded by the 2 nd flow control device 62 b.

Most of the merged liquid refrigerant is expanded by the 1 st flow rate control device 62a, and becomes a low-temperature low-pressure two-phase gas-liquid refrigerant. The remaining part of the merged liquid refrigerant is expanded by the 4 th expansion device 68, and becomes a low-temperature low-pressure gas-liquid two-phase refrigerant. At this time, the opening degree of the 4 th throttle device 68 is controlled such that: the degree of superheat (superheat) obtained by using the difference between the temperature detected by the inlet temperature sensor 89 and the temperature detected by the outlet temperature sensor 90 is made constant. Then, the low-temperature low-pressure gas-liquid two-phase refrigerant exchanges heat with the high-pressure liquid refrigerant in the inter-refrigerant heat exchanger 60 to become a low-temperature low-pressure gas refrigerant, and then flows into the low-pressure piping on the outlet side of the relay device 6.

Next, the operation of the secondary side cycle in the heating main operation mode will be described. In the secondary-side cycle, for example, the indoor units 2a to 2b perform a heating operation, and the indoor unit 2c performs a cooling operation. First, the indoor units 2a to 2b that perform the heating operation in the heating main operation mode will be described. The coolant pressurized by the 1 st pump 65a flows into the 1 st intermediate heat exchanger 63 a. The coolant having a high temperature in the 2 nd intermediate heat exchanger 63b passes through the 1 st flow switching devices 66a to 66b set in a state of being communicated with the 2 nd intermediate heat exchanger 63b, and flows into the load side heat exchangers 21a to 21 b. The coolant flowing through the load side heat exchangers 21a to 21b heats the indoor air and heats the air. During heating, the coolant is cooled by the indoor air and returned to the 2 nd pump 65b in the relay device 6 through the 2 nd flow switching devices 67a to 67 b. At this time, the voltage of the 2 nd pump 65b is controlled to: for example, the difference between the temperature detected by the indoor unit inlet temperature sensor 94b and the temperature detected by the indoor unit outlet temperature sensor 93b is made constant.

Next, a description will be given of the indoor unit 2c that performs the heating operation in the heating-main operation mode. The coolant pressurized by the 1 st pump 65a flows into the 1 st intermediate heat exchanger 63 a. The coolant having a low temperature in the 1 st intermediate heat exchanger 63a passes through the 1 st flow switching device 66c set in a state of being communicated with the 1 st intermediate heat exchanger 63a, and flows into the load side heat exchanger 21 c. The coolant flowing through the load side heat exchanger 21c cools the indoor air and performs cooling. During cooling, the brine is heated by the indoor air and returns to the 1 st pump 65a in the relay device 6 through the 2 nd flow switching device 67 c. At this time, the voltage of the 1 st pump 65a is controlled to: for example, the difference between the temperature detected by the indoor unit inlet temperature sensor 94a and the temperature detected by the indoor unit outlet temperature sensor 93a is made constant.

As described above, in the air conditioning apparatus 300 shown in fig. 19 to 23, in the cooling only operation mode, the cooling main operation mode, the heating only operation mode, and the heating main operation mode, as in the air conditioning apparatus 100 shown in fig. 1 to 4, a part of the refrigerating machine oil and the gas refrigerant separated by the oil separator 11 is cooled, and thereby the injection into the suction portion of the compressor 10 can be performed via the 1 st flow rate adjusting device 72.

Embodiment 9.

Fig. 24 is a diagram schematically illustrating an example of a circuit configuration of an air conditioning apparatus according to embodiment 9 of the present invention. In the air conditioner 301 of fig. 24, the same reference numerals are given to parts having the same configuration as the air conditioner 300 of fig. 19, and the description thereof is omitted. In the air conditioner 301 of fig. 24, the outdoor unit 1 has a different configuration from the air conditioner 300 of fig. 19. That is, the outdoor unit 1 of the example of the present embodiment further includes a flow rate adjuster 73 arranged in parallel with the 1 st flow rate adjuster 72. The flow rate adjuster 73 is constituted by a device such as a capillary tube to which a flow path resistance value is fixed.

In the air conditioner 301, for example, when the discharge temperature of the compressor 10 detected by the discharge temperature sensor 80 is equal to or lower than the discharge temperature threshold, the controller 97 controls the 1 st flow rate adjusting device 72 so that the 1 st flow rate adjusting device 72 is in the fully-closed state. The discharge temperature threshold value is, for example, a temperature lower than a temperature at which the compressor 10 is at risk of damage or a temperature at which the refrigerator oil is at risk of degradation, and is set to, for example, 115 degrees or less. The discharge temperature threshold value is set in advance in accordance with a limit value of the discharge temperature of the compressor 10 or the like, and is stored in, for example, a storage unit (not shown).

As described above, since the outdoor unit 1 of the present embodiment includes the flow rate adjuster 73 arranged in parallel with the 1 st flow rate adjuster 72, even when the 1 st flow rate adjuster 72 is in an abnormal state and is in a closed state, the refrigerating machine oil or the refrigerating machine oil and the refrigerant circulate in the order of the compressor 10, the oil separator 11, the auxiliary heat exchanger 71, the flow rate adjuster 73, and the compressor 10. Therefore, even when the 1 st flow rate adjustment device 72 is in the closed state due to an abnormality, the refrigerating machine oil in an amount that does not cause the refrigerating machine oil in the compressor 10 to be depleted flows into the suction portion of the compressor 10 through the auxiliary heat exchanger 71 and the flow rate adjuster 73. Therefore, according to the outdoor unit 1 of the example of the present embodiment, even when the 1 st flow rate adjustment device 72 is in the closed state due to an abnormality, it is possible to secure the amount of the refrigerating machine oil necessary for lubrication and sealing of the compressor 10 while suppressing an increase in the discharge temperature of the compressor 10. Therefore, according to the outdoor unit 1 of the example of the present embodiment, the risk of damage to the compressor 10 can be reliably suppressed.

Embodiment 10.

Fig. 25 is a diagram schematically illustrating an example of the circuit configuration of an air conditioning apparatus according to embodiment 10 of the present invention. In the air conditioner 302 of fig. 25, the same reference numerals are given to parts having the same configuration as the air conditioner 301 of fig. 24, and the description thereof is omitted. In the air conditioner 302 of fig. 25, the outdoor unit 1 is different in configuration from the air conditioner 301 of fig. 24. That is, the outdoor unit 1 of the present embodiment further includes the 2 nd bypass flow path 74 in which the 2 nd flow rate adjusting device 75 is disposed. One end of the 2 nd bypass passage 74 is connected to a pipe between the heat source side heat exchanger 13 and the main pipe 3 through which the liquid refrigerant flows in any of the cooling only operation mode, the cooling main operation mode, the heating only operation mode, and the heating main operation mode, and the other end is connected to the outflow side of the 1 st flow control device 72. That is, the 2 nd bypass passage 74 bypasses the pipe connecting the heat source side heat exchanger 13 and the load

side expansion devices

20a and 20b and the intake side of the compressor 10. The 2 nd bypass passage 74 is a pipe through which a low-temperature and high-pressure liquid refrigerant flows into the suction portion of the compressor 10 during the cooling operation, and a medium-temperature and medium-pressure liquid refrigerant or a two-phase refrigerant flows into the suction portion of the compressor 10 during the heating operation. The 2 nd flow rate adjusting device 75 is composed of a device such as an electronic expansion valve, for example, which can variably control the opening degree, and adjusts the flow rate of the liquid refrigerant or the two-phase refrigerant flowing into the suction portion of the compressor 10.

side throttling devices

As described above, in the air-conditioning apparatus 302 of the example of the present embodiment, in any of the cooling only operation mode, the cooling main operation mode, the heating only operation mode, and the heating main operation mode, the suction enthalpy of the compressor 10 can be reduced by the fluid cooled by the auxiliary heat exchanger 71, and the suction enthalpy of the compressor 10 can be reduced by a part of the refrigerant cooled by the heat source side heat exchanger 13. Therefore, according to the air conditioner 302 of the example of the present embodiment, when the discharge temperature of the compressor 10 increases, the increase in the discharge temperature of the compressor 10 can be suppressed. That is, for example, even when the heat exchange capacity, which is the processing capacity of the auxiliary heat exchanger 71, reaches the upper limit, the 2 nd flow rate adjustment device 75 can be turned on to suppress the increase in the discharge temperature of the compressor 10. According to the air conditioner 302 of the example of the present embodiment, since an increase in the discharge temperature of the compressor 10 can be suppressed, degradation of the refrigerating machine oil and damage to the compressor 10 can be suppressed. Further, since the refrigerating machine oil in the suction portion of the compressor 10 can be reliably cooled, the loss due to the suction heating of the compressor 10 can be suppressed. Furthermore, since the increase in the discharge temperature of the compressor 10 is suppressed, the rotational speed of the compressor 10 can be increased, and the intensity of cooling can be increased.

Fig. 26 is a diagram schematically showing the configuration of the control device of the air conditioner according to embodiments 1 to 10 of the present invention. As shown in fig. 26, the control device 97 includes an acquisition unit 97-1 that acquires outputs of various sensors, a flow rate adjustment device control unit 97-2 that adjusts the opening degree of the 1 st flow rate adjustment device 72 or the opening degree of the 2 nd flow rate adjustment device 75 using the detection results of the various sensors acquired by the acquisition unit 97-1, and a storage unit 97-3 that stores parameters for adjusting the opening degree of the 1 st flow rate adjustment device 72 or the opening degree of the 2 nd flow rate adjustment device 75, and the like.

As described above, the air conditioning apparatus according to embodiments 1 to 10 includes: a refrigerant circuit 15 in which the compressor 10, the heat source side heat exchanger 13, the expansion device 20, and the load side heat exchanger 21 are connected by piping to the refrigerant circuit 15, and a refrigerant circulates; and a 1 st bypass flow path 70 that bypasses a discharge side of the compressor 10 and a suction side of the compressor 10; an auxiliary heat exchanger 71 disposed in the 1 st bypass passage 70 and cooling the refrigerant; a 1 st flow rate adjusting device 72 disposed in the 1 st bypass flow path 70 and controlling the passage of the refrigerant by adjusting the opening degree; and a discharge temperature sensor 80 that detects the temperature of the refrigerant discharged from the compressor 10, wherein the opening degree of the 1 st flow rate adjusting device 72 is made larger when the temperature detected by the discharge temperature sensor 80 is higher than a discharge target temperature value that is a target temperature at the time when the refrigerant is discharged from the compressor 10, and the opening degree of the 1 st flow rate adjusting device 72 is made smaller when the temperature detected by the discharge temperature sensor 80 is lower than the discharge target temperature value. Preferably, a bypass passage 78 is further provided, which is connected in parallel with the 1 st flow regulator 72. Preferably, the flow rate regulator 73 is disposed in the bypass passage 78 and controls the passage of the refrigerant, and the flow rate regulator 73 has a flow path resistance smaller than the flow path resistance of the 1 st flow rate regulator 72 when the opening degree of the 1 st flow rate regulator 72 is in the fully open state. Further, it is preferable that an oil separator 11 is further provided, the oil separator 11 is disposed in a pipe connecting the compressor 10 and the expansion device 20, the refrigerator oil is separated from the refrigerant discharged from the compressor 10, and the discharge side of the compressor 10 of the 1 st bypass passage 70 is connected to the oil separator 11. Preferably, the heat exchanger further includes an auxiliary heat exchanger outlet temperature sensor 83 for detecting the temperature of the fluid having exchanged heat in the auxiliary heat exchanger 71, and an outside air temperature sensor 96 for detecting the temperature of the air before exchanging heat in the heat source side heat exchanger 13, when the difference between the temperature detected by the auxiliary heat exchanger outlet temperature sensor 83 and the temperature detected by the outside air temperature sensor 96 is greater than the threshold value, the opening degree of the 1 st flow rate adjusting device 72 is fixed, when the difference between the temperature detected by the auxiliary heat exchanger outlet temperature sensor 83 and the temperature detected by the outside air temperature sensor 96 is smaller than the threshold value, the opening degree of the 1 st flow rate adjusting device 72 is increased when the temperature detected by the discharge temperature sensor 80 is higher than the discharge target temperature value, when the temperature detected by the discharge temperature sensor 80 is lower than the discharge target temperature value, the opening degree of the 1 st flow rate adjusting device 72 is decreased. Preferably, the cooling system further includes a condensation temperature detection device that obtains a condensation temperature of the refrigerant, and the threshold value is a value equal to or less than a difference between the condensation temperature obtained by the condensation temperature detection device and the temperature detected by the outside air temperature sensor 96. It is preferable that a 2 nd bypass passage 74 be further provided, and the 2 nd bypass passage 74 bypasses the suction side of the compressor 10 and a pipe connecting the heat source side heat exchanger 13 and the expansion device 20. Preferably, the refrigerant circulation device further includes a 2 nd flow rate adjustment device 75 which is disposed in the 2 nd bypass flow path 74 and controls the passage of the refrigerant by adjusting the opening degree. Further, it is preferable that a pressure adjusting device 76 for adjusting the pressure of the refrigerant is disposed in the piping connecting the heat source side heat exchanger 13 and the expansion device 20, at a position closer to the heat source side heat exchanger 13 than the connection portion connecting the 2 nd bypass passage 74. It is preferable that the opening degree of the 1 st flow rate adjustment device 72 or the 2 nd flow rate adjustment device 75 is increased when the temperature detected by the discharge temperature sensor 80 is higher than the discharge target temperature value, and the opening degree of the 1 st flow rate adjustment device 72 or the 2 nd flow rate adjustment device 75 is decreased when the temperature detected by the discharge temperature sensor 80 is lower than the discharge target temperature value. Preferably, the opening degree of the 2 nd flow rate adjusting device 75 is adjusted when the difference between the temperature detected by the auxiliary heat exchanger outlet temperature sensor 83 and the temperature detected by the outside air temperature sensor 96 is greater than a threshold value. With the above configuration, according to the present invention, an air conditioner in which an increase in the discharge temperature of the compressor 10 is suppressed can be obtained.

The present invention is not limited to the above-described embodiments, and various changes can be made within the scope of the present invention. That is, the structure of the above embodiment can be appropriately modified, and at least a part of the structure can be replaced with another structure. Further, the components not particularly limited in their arrangement are not limited to the arrangement disclosed in the embodiment, and can be arranged at positions that can achieve their functions.

For example, in the above description, the case where the discharge temperature threshold is 115 degrees in the cooling operation mode and the heating operation mode has been exemplified, but the discharge temperature threshold may be set according to, for example, a limit value of the discharge temperature of the compressor 10.

For example, when the limit value of the discharge temperature of the compressor 10 is 120 degrees, the operation of the compressor 10 is controlled by the controller 97 so that the discharge temperature of the compressor 10 does not exceed 120 degrees. For example, when the discharge temperature of compressor 10 exceeds 110 degrees, control device 97 controls to reduce the frequency of compressor 10 to decelerate compressor 10. In this way, when the limit value of the discharge temperature of the compressor 10 is 120 degrees and the compressor 10 is decelerated when the discharge temperature of the compressor 10 exceeds 110 degrees, the discharge temperature threshold value may be set to a temperature (for example, 105 degrees or the like) from 110 degrees to 100 degrees, which is a temperature slightly lower than 110 degrees, which is a threshold value for reducing the frequency of the compressor 10.

For example, in the case where the limit value of the discharge temperature of the compressor 10 is 120 degrees and the compressor 10 is not decelerated when the discharge temperature of the compressor 10 exceeds 110 degrees, the discharge temperature threshold value may be set to be from 120 degrees to 100 degrees (for example, 115 degrees or the like).

For example, the refrigerant applied to the air conditioner of the above embodiment is not limited to R32, and may be a mixed refrigerant containing R32, or the like. The mixed refrigerant containing R32 is, for example, a mixed refrigerant (non-azeotropic mixed refrigerant) including R32, HFO1234yf, HFO1234ze, and the like. HFO1234yf, HFO1234ze and the like have chemical formulas represented by CF₃CF＝CH₂The tetrafluoropropene-based refrigerant is a refrigerant having a low global temperature coefficient of thermal expansion. It is known that the discharge temperature of the compressor 10 of the R32 or the refrigerant containing R32 is increased by about 20 degrees compared to that of the R410A in the same operation state of the compressor 10.

For example, it is known that in a mixed refrigerant of R32 and HFO1234yf, when the mass ratio of R32 is 62% (62 wt%) or more, the discharge temperature of the compressor is increased by 3 degrees or more as compared with the case of using R410A.

In addition, for example, in the mixed refrigerant of R32 and HFO1234ze, in the case where the mass ratio of R32 is 43% (43 wt%) or more, the discharge temperature is increased by 3 degrees or more as compared with the case where R410A is used.

The air conditioner described in the above embodiment can lower the discharge temperature of the compressor, and the effect is remarkable in the air conditioner using the refrigerant that increases the discharge temperature of the compressor as described above.

The refrigerant having a high discharge temperature of the compressor is not limited to the refrigerant containing R32, and includes, for example, CO₂(R744) and the like are supercritical refrigerants.

For example, in the air-conditioning apparatus of the above-described embodiment, the example in which the auxiliary heat exchanger 71 and the heat source side heat exchanger 13 are integrally configured has been described, but the auxiliary heat exchanger 71 and the heat source side heat exchanger 13 may be separately configured. In the air-conditioning apparatus of the above-described embodiment, the example in which the auxiliary heat exchanger 71 is disposed below and the heat source side heat exchanger 13 is disposed above has been described, but the auxiliary heat exchanger 71 may be disposed above and the heat source side heat exchanger 13 may be disposed below.

In embodiments 5 to 8, an example of an air conditioner in which the outdoor unit 1 and the relay devices 5 and 6 are connected to each other using 2 main pipes 3 has been described, but the above embodiments 5 to 8 are not limited to this. For example, the outdoor unit 1 and the relay devices 5 and 6 may be connected to each other by using 3 main pipes.

For example, in the above-described embodiment, the example in which the compressor 10 is configured by the low-pressure shell-type compressor has been described, but the compressor 10 may be a high-pressure shell-type compressor.

For example, generally, a blower that promotes condensation or evaporation of refrigerant by blowing air is often provided in the vicinity of the heat source-side heat exchanger and the load-side heat exchanger, and in the above-described embodiment, an example in which a blower is provided in the vicinity of the heat source-side heat exchanger, the auxiliary heat exchanger, and the load-side heat exchanger has been described, but the above-described embodiment is not limited to this. For example, a radiant heater using radiation may be used as the load side heat exchanger. Further, as the heat source side heat exchanger and the auxiliary heat exchanger, a type of heat exchanger that exchanges heat between the refrigerant and a liquid such as water or an antifreeze can be used. That is, the heat source-side heat exchanger, the auxiliary heat exchanger, and the load-side heat exchanger may be any heat exchangers as long as the heat release or the heat absorption of the refrigerant is possible. As a type of heat exchanger for exchanging heat between a refrigerant and a liquid such as water or an antifreeze, for example, a plate heat exchanger is used.

Further, the description has been given of a direct expansion type air conditioner in which the refrigerant circulates by connecting the outdoor unit 1 and the indoor unit 2 by pipes, a direct expansion type air conditioner in which the refrigerant circulates by connecting the outdoor unit 1, the relay unit 5, and the indoor unit 2 by pipes, and an indirect type air conditioner in which the refrigerant circulates by connecting the outdoor unit 1 and the relay unit 6 by pipes, and the brine circulates by connecting the relay unit 6 and the indoor unit 2 by pipes, but the present invention is not limited thereto. For example, the above embodiment can be applied to an air conditioner including: the refrigerant is circulated only in the outdoor unit, the brine is circulated among the outdoor unit, the relay device, and the indoor units, and heat exchange between the refrigerant and the heat medium is performed in the outdoor unit, thereby performing air conditioning. In addition, although the above-described embodiments have been described with respect to the case of using the indoor unit for heating (heating operation) and cooling (cooling operation), the present invention may be used instead of the indoor unit: heat exchange between the refrigerant and water or the like is performed, and hot water is generated by a heating operation or cold water is generated by a cooling operation.

Description of the symbols

1 outdoor unit, 2 indoor units, 2a indoor unit, 2b indoor unit, 2c indoor unit, 3 main pipe, 4 refrigerant piping, 4a branch pipe, 4b branch pipe, 4c branch pipe, 5 relay device, 6 relay device, 10 compressor, 11 oil separator, 12 refrigerant flow switching device, 13 heat source side heat exchanger, 14 fan, 15 refrigerant circuit, 16 accumulator, 16b 1 st backflow prevention device, 16d 1 st backflow prevention device, 17 suction piping, 18a 1 st connection piping, 18b 2 nd connection piping, 19 compressor, 19a 1 st backflow prevention device, 19b 1 st backflow prevention device, 19c 1 st backflow prevention device, 19d 1 st backflow prevention device, 20 load side throttling device, 20a load side throttling device, 20b load-side expansion device, 20c load-side expansion device, 21 load-side heat exchanger, 21a load-side heat exchanger, 21b load-side heat exchanger, 21c load-side heat exchanger, 22 fan, 22a fan, 22b fan, 22c fan, 50 gas-liquid separator, 51 rd 3 expansion device, 52 refrigerant-to-refrigerant heat exchanger, 53 st 1 switching device, 53a 1 st switching device, 53b 1 st switching device, 53c 1 st switching device, 54a 2 nd switching device, 54b 2 nd switching device, 54c 2 nd switching device, 55a 2 nd reverse-flow preventing device, 55b 2 nd reverse-flow preventing device, 55c 2 nd reverse-flow preventing device, 56a 3 rd reverse-flow preventing device, 56b 3 rd reverse-flow preventing device, 56c 3 rd reverse-flow preventing device, 57 th 4 th expansion device, 60 refrigerant-to-refrigerant heat exchanger, 61 rd 3 throttle device, 62a 1 st flow rate control device, 62b 2 nd flow rate control device, 63a 1 st intermediate heat exchanger, 63b 2 nd intermediate heat exchanger, 64a 1 st flow path switching device, 64b 2 nd flow path switching device, 65a 1 st pump, 65b 2 nd pump, 66a 1 st flow path switching device, 66b 1 st flow path switching device, 66c 1 st flow path switching device, 67a 2 nd flow path switching device, 67b 2 nd flow path switching device, 67c 2 nd flow path switching device, 68 th 4 th throttle device, 70 th 1 st bypass flow path, 71 auxiliary heat exchanger, 72 th 1 flow rate adjustment device, 73 nd flow rate adjuster, 74 nd 2 nd bypass flow path, 75 nd 2 nd flow rate adjustment device, 76 pressure adjustment device, 77 middle pressure detection sensor, 78 bypass, 79 high pressure detection sensor, 80 discharge temperature sensor, 81 refrigerating machine oil temperature sensor, 82 low pressure detection sensor, 83 auxiliary heat exchanger outlet temperature sensor, 84 outlet side temperature sensor, 84a outlet side temperature sensor, 84b outlet side temperature sensor, 84c outlet side temperature sensor, 85 inlet side temperature sensor, 85a inlet side temperature sensor, 85b inlet side temperature sensor, 85c inlet side temperature sensor, 86 inlet side pressure sensor, 86a outlet side temperature sensor, 86b outlet side temperature sensor, 87 outlet side pressure sensor, 88 temperature sensor, 89 inlet temperature sensor, 90 outlet temperature sensor, 91a inlet temperature sensor, 91b inlet temperature sensor, 92a outlet temperature sensor, 92b outlet temperature sensor, 93a indoor unit outlet temperature sensor, 93b indoor unit outlet temperature sensor, 94a indoor unit inlet temperature sensor, 94b indoor unit inlet temperature sensor, 95a indoor unit outlet temperature sensor, 95b indoor unit outlet temperature sensor, 95c indoor unit outlet temperature sensor, 95d indoor unit outlet temperature sensor, 96 outside air temperature sensor, 97 control device, 97-1 acquisition unit, 97-2 flow rate adjustment device control unit, 97-3 storage unit, 98 outlet pressure sensor, 100 air conditioner, 101 air conditioner, 102 air conditioner, 200 air conditioner, 201 air conditioner, 202 air conditioner, 300 air conditioner, 301 air conditioner, 302 air conditioner, ET condensation temperature, G1 control constant, G2 control constant, G3 control constant, G4 control constant, O1con operation amount, O1d 1 st flow regulator current opening, O1n output opening, O1nex output opening, O1op correction opening, O2con operation amount, O2d nd flow regulator current opening, O2n output opening, O2nex output opening, O2op correction opening, OILsh refrigerator oil superheat threshold, Ocon operation amount, Od opening, On output opening, Onex output opening, Oop correction opening, Osh refrigerator oil superheat, Ps discharge side pressure, SHoil refrigerator oil superheat target value, T1 auxiliary heat exchanger outlet side temperature, Ta refrigerator outside temperature, Td discharge temperature, Tdn target discharge temperature, Toil oil temperature, Tth temperature difference threshold, Δ ol refrigerator oil correction amount, Δ oi refrigerator oil correction amount, Δ oih refrigerator oil 829 correction amount, Δ Osh refrigerator oil superheat difference, The Δ T temperature difference, Δ Td discharges the temperature adjustment amount.

Claims

1. An air conditioning device is provided with:

a refrigerant circuit in which a compressor, a flow switching device, a heat source side heat exchanger, a throttle device, a load side heat exchanger, and the flow switching device are connected in this order by piping, and an operation is performed such that the flow switching device can switch between a cooling operation in which a discharge side of the compressor is connected to the heat source side heat exchanger and a suction side of the compressor is connected to the load side heat exchanger, and a heating operation in which a discharge side of the compressor is connected to the load side heat exchanger and a suction side of the compressor is connected to the heat source side heat exchanger;

an oil separator disposed in the pipe connecting the discharge portion of the compressor and the flow path switching device, for separating the refrigerating machine oil from the refrigerant discharged from the compressor;

a 1 st bypass flow path which is connected to an oil outflow side of the oil separator and an intake portion of the compressor and which introduces a fluid flowing out of the oil separator;

an auxiliary heat exchanger disposed in the 1 st bypass passage and cooling the fluid;

a 1 st flow rate adjusting device disposed in the 1 st bypass flow path and controlling passage of the fluid;

a 2 nd bypass passage connected to the pipe connecting the heat source side heat exchanger and the expansion device and the pipe connecting the suction portion of the compressor and the passage switching device, and configured to introduce a liquid refrigerant or a two-phase refrigerant of a liquid and a gas flowing through the pipe connecting the heat source side heat exchanger and the expansion device;

a 2 nd flow rate adjusting device disposed in the 2 nd bypass flow path and controlling the passage of the refrigerant;

a discharge temperature sensor that detects a temperature of the refrigerant discharged from the compressor;

a control device that controls an opening degree of the 1 st or 2 nd flow rate adjustment device based on the discharge temperature detected by the discharge temperature sensor;

a pressure adjusting device that is disposed in the pipe connecting the heat source-side heat exchanger and the expansion device, at a position closer to the heat source-side heat exchanger than a connection portion connecting the 2 nd bypass passage, and that adjusts the pressure of the refrigerant;

an auxiliary heat exchanger outlet temperature sensor that detects a temperature of the fluid that has exchanged heat in the auxiliary heat exchanger; and

an outside air temperature sensor that detects a temperature of air before heat exchange in the heat source-side heat exchanger;

the control device controls to: increasing the opening degree of the 1 st or 2 nd flow rate adjustment device when the temperature detected by the discharge temperature sensor is higher than a discharge temperature target value that is a target temperature at the time of discharging the refrigerant from the compressor;

reducing the opening degree of the 1 st or 2 nd flow rate adjustment device when the temperature detected by the discharge temperature sensor is lower than the discharge temperature target value,

the control device determines whether or not to control the 1 st flow rate adjustment device based on a difference between a temperature detected by the auxiliary heat exchanger outlet temperature sensor and a temperature detected by the outside air temperature sensor during a cooling operation.

2. The air conditioner according to claim 1,

the air conditioner further includes an accumulator disposed on the flow path switching device side of a connection portion connecting the 1 st bypass flow path and the 2 nd bypass flow path in the pipe connecting the suction portion of the compressor and the flow path switching device.

3. The air conditioner according to claim 1,

the control device controls the 1 st flow rate adjustment device when a difference between the temperature detected by the auxiliary heat exchanger outlet temperature sensor and the temperature detected by the outside air temperature sensor is smaller than a threshold value, and does not control the 1 st flow rate adjustment device when the difference between the temperature detected by the auxiliary heat exchanger outlet temperature sensor and the temperature detected by the outside air temperature sensor is larger than the threshold value.

4. The air conditioner according to claim 1,

the control device controls the 1 st flow rate adjustment device when a difference between a temperature detected by the auxiliary heat exchanger outlet temperature sensor and a temperature detected by the outside air temperature sensor is smaller than a threshold value during the cooling operation, and controls the 2 nd flow rate adjustment device when a difference between a temperature detected by the auxiliary heat exchanger outlet temperature sensor and a temperature detected by the outside air temperature sensor is larger than the threshold value.

5. Air conditioning unit according to claim 3 or 4,

the air conditioner further includes a high pressure detection sensor that obtains a discharge pressure of the refrigerant discharged from the compressor;

the threshold value is a value equal to or less than a difference between a condensation temperature calculated based on the discharge pressure detected by the high-pressure detection sensor and a temperature detected by the outside air temperature sensor.

6. Air conditioning unit according to any one of claims 1 to 4,

the air conditioning apparatus further includes a medium pressure detection sensor that detects a pressure of the refrigerant between the throttle device and the pressure adjustment device;

the control device controls the pressure adjusting device such that the intermediate pressure detected by the intermediate pressure detection sensor during the heating operation is higher than the pressure of the pipe between the suction portion of the compressor and the flow path switching device.

7. Air conditioning unit according to any one of claims 1 to 4,

the control device controls the 1 st flow rate adjustment device and the 2 nd flow rate adjustment device during the cooling operation, and controls the 2 nd flow rate adjustment device during the heating operation.

8. Air conditioning unit according to any one of claims 1 to 4,

the air conditioner further includes a bypass passage connected in parallel to the 1 st flow rate adjusting device.

9. Air conditioning unit according to claim 8,

the air conditioner further includes a flow rate regulator disposed in the bypass passage and configured to control the passage of the refrigerant;

the flow rate adjuster has a flow path resistance smaller than a flow path resistance of the 1 st flow rate adjuster when the opening degree of the 1 st flow rate adjuster is in a fully open state.